RU2752114C1 - Roticulating thermodynamic device - Google Patents

Abstract

FIELD: thermodynamics.SUBSTANCE: invention relates to a roticulating thermodynamic device. The device (100) is made with the first flow path (111) and the second flow path (115). Part (111) is configured to allow fluid to pass from the first port (114a) to the second port (114b) through the first chamber (134a). Part (115) is configured to allow fluid to pass from the third port (116a) to the fourth port (116b) through the second chamber (134b). The port (114b) is in fluid communication with the port (116a) through the first heat exchanger (302a).EFFECT: invention is aimed at providing ability to operate in a wide range of operating rotation frequencies and/or temperature differences with fewer restrictions, lower losses and higher efficiency.28 cl, 28 dwg

Description

The technical field to which the invention relates

The present disclosure relates to a rotational thermodynamic device.

In particular, the disclosure relates to a thermodynamic device configured to function as a heat pump and / or a heat engine.

State of the art

The prototype of the invention is known from the publication US 2002/112485 A1, publ. 22.08.2002, IPC index F25B9 / 00. One of the analogues of the invention is known from GB 2544819 A, publ. 05/31/2017, IPC index F04C9 / 00.

Known heat pumps and heat engines for compressing and expanding a working fluid often include a pump for increasing the pressure of the working fluid and a turbine for expanding the fluid. This is due to the fact that among the known thermodynamic expanders, the most effective devices are of the rotary type (for example, turbines), while the expansion ratio they provide in one stage is usually limited to 3: 1.

To optimize system performance, the operating speed of the turbine is generally higher than the operating speed of the pump. Therefore, the pump and turbine are usually of different types and rotate independently of each other to enable them to operate at different speeds from each other.

In addition, in order to achieve the maximum efficiency of the known pump and turbine units, constant operating speeds are required. The very nature of most systems dictates that they usually need to be optimized for a relatively narrow operating range, beyond which operation can cause significant inefficiencies or unacceptable wear on components.

This means that a large temperature difference is required to achieve sufficiently high operating speeds of a known heat pump or known heat engine, which in turn means that such devices cannot operate in an environment where only lower temperature differences are possible. This limits the effectiveness of such prior art devices.

Therefore, there is a need for a heat pump or motor capable of operating over a wide range of operating speeds and / or temperature differences with fewer restrictions, lower losses and higher efficiency.

The essence of the invention

According to the present disclosure, there is provided an apparatus and method as indicated in the appended claims. Further features of the invention will become apparent from the dependent claims and the following description.

Accordingly, a rotational thermodynamic device (100) with a first flow path (111) can be provided, comprising: a first shaft portion (118) defining a first rotation axis (130) and rotatable about it; a first technical axis (120) defining a second axis of rotation (132), the first shaft portion (118) passing through the first technical axis (120); a first piston element (122a) located on a first shaft portion (118), the first piston element (122a) extending from a first technical axis (120) to a distal end of the first shaft portion (118); the first rotor (119) carried by the first technical axle (120); wherein the first rotor (119) comprises: a first chamber (134a), wherein the first piston element (122a) passes through the first chamber (134a); a first casing wall adjacent to the first chamber (134a), a first window (114a) and a second window (114b) located in the casing wall, each in fluid communication with the first chamber (134a); in such a way that: the first rotor (119) and the first technical axis (120) are made with the possibility of rotation with the first shaft part (118) about the first axis (130) of rotation; wherein the first rotor (119) is rotatable relative to the technical axis (120) around the second axis (132) of rotation to provide the first rotor (119) with the possibility of rotation relative to the first piston element (122a) when the first rotor (119) rotates around the first axis (130) rotation; the first flow path (111) is configured to allow fluid to pass from the first port (114a) to the second port (114b) through the first chamber (134a); the device further comprises a second flow part (115), comprising: a second chamber (134b, 234b), a second casing wall adjacent to the second chamber (134b, 234b), a third window (116a) and a fourth window (116b) located in the second wall of the casing, each of them being in fluid communication with the second chamber (134b, 234b), whereby the second flow path (115) is configured to allow fluid to pass from the third window (116a) to the fourth window (116b) through the second chamber (134, 234b); wherein the second port (114b) is in fluid communication with the third port (116a) through the first heat exchanger (302a).

The second axis of rotation (132) may be substantially perpendicular to the first axis of rotation (130).

The first rotor (119) may include a second chamber (134b). The first piston element (122a) may extend from one side of the first technical axis (120) along the first shaft portion (118). The second piston element (122b) can extend from the other side of the first technical axis (120) along the first shaft portion (118) through the second chamber (134b) to allow the first rotor (119) to rotate relative to the second piston element (122b) when the first rotor rotates. (119) around the first axis (130) of rotation.

The fourth port (116b) may be in fluid communication with the first port (114a) via a second heat exchanger (306a).

The volumetric capacity of the first chamber (134a) of the first rotor may be substantially equal to, less than or greater than, the volumetric capacity of the second chamber (134b) of the first rotor.

The first shaft part (118), the first technical axis (120) and the first piston element (s) (122a) can be stationary relative to each other.

The device (200) may additionally comprise: a second rotor (219) containing a second chamber (234b), a second shaft part (218) rotatable about the first axis of rotation (130); wherein the second shaft part (218) is connected to the first shaft part (118) so that the first shaft part (118) can rotate together with the second shaft part (218) about the first rotation axis (130). It is also possible to create a second technical axis (220), forming a third axis (232) of rotation, with the second shaft part (218) passing through the second technical axis (220); a second piston element (222b) located on a second shaft portion (218), the second piston element (222b) extending from the second technical axis (220) towards the distal end of the second shaft part (218); the second rotor (219) carries the second technical axis (220); while the second piston element (222b) passes through the second chamber (234b); due to which: the second rotor (219) and the second technical axis (220) are made with the possibility of rotation with the second shaft part (218) around the first axis (130) of rotation; wherein the second rotor (219) is rotatable relative to the second technical axis (220) around the third axis (232) of rotation to provide the second rotor (219) with the possibility of rotation relative to the second piston element (222) when the second rotor (219) rotates around the second axis (130) of rotation.

The third axis of rotation (232) may be substantially perpendicular to the first axis of rotation (130).

The first rotor (119) may comprise: a second chamber (134b) of the first rotor, wherein the first piston element (122a) extends from one side of the first technical axis (120) along the first shaft portion (118); while the second piston element (122b) extends from the other side of the first technical axis (120) along the first shaft part (118), through the second chamber (134b) of the first rotor to allow the first rotor (119) to rotate relative to the second piston element (122b) when the first rotor (119) rotates around the first rotation axis (130). The second rotor (219) may comprise: a first chamber (234a) of the second rotor, wherein the second piston element (222b) extends from one side of the second technical axis (220) along the second shaft portion (218); wherein the first piston element (222a) of the second rotor extends from the other side of the second technical axis (220) along the second shaft part (218), through the first chamber (234a) of the second rotor to provide the second rotor (219) with the possibility of rotation relative to the first piston element ( 222a) of the second rotor as the second rotor (219) rotates around the first axis of rotation (130). The second chamber (134b) of the first rotor may be in fluid communication with: the fifth port (114c) and the sixth port (114d); for entering, due to this, in the composition of the first flow part (111), and is made with the possibility of passage of fluid from the fifth port (114c) to the sixth port (114d) through the second chamber (134b) of the first rotor; the first chamber (234a) of the second rotor is in fluid communication with the seventh window (116c) and the eighth window (116d); for entering, due to this, in the composition of the second flow part (115), and is made with the possibility of passing the fluid from the seventh port (116c) to the eighth port (116d) through the second chamber (234b) of the second rotor; wherein the sixth port (114d) is in fluid communication with the seventh port (116c) through the first heat exchanger (302a).

The eighth port (116d) may be in fluid communication with the fifth port (114c) via a second heat exchanger (306a).

The fourth port (116b) may be in fluid communication with the first port (114a) via a second heat exchanger (306a).

The first chamber (134a) and the second chamber (134b) of the first rotor (119) may have substantially equal volumetric capacity; the first chamber (234a) and the second chamber (234b) of the second rotor (219) have substantially equal volumetric capacity; wherein the volumetric capacity of the chambers (134a, 134b) of the first rotor is substantially equal to, less than or greater than, the volumetric capacity of the chambers (234a, 234b) of the second rotor.

The first shaft part (118) can be directly connected to the second shaft part (218), in connection with which the first rotor (119) and the second rotor (219) are configured to rotate only at the same frequency.

The second shaft part (218), the second technical axis (220) and the second piston element (s) (222b) can be stationary relative to each other.

The first heat exchanger (302a) may be configured to function as a heat sink for extracting thermal energy from a fluid passing through it.

The second heat exchanger (306a) may be configured to function as a heat source for transferring thermal energy to a fluid passing therethrough.

The first heat exchanger (302a) may include a chamber (810) configured to pass a fluid flow from the first flow path (112) to the second flow path (115); and a nozzle (812) configured to inject a cryogenic medium into the chamber (810), thereby transferring thermal energy from the fluid to the cryogenic media.

The first heat exchanger (302a) may be configured to function as a heat source for transferring thermal energy to a fluid passing therethrough.

The second heat exchanger (306a) may be configured to function as a heat sink for extracting thermal energy from a fluid passing through it.

The first heat exchanger (302a) may comprise: a combustion chamber configured to burn continuously.

The chamber or each of the chambers (134a, 134b, 234a, 234b) may have an opening (36); the corresponding piston element (122a, 122b, 222a, 222b) or each of them extends from its technical axis (20) through the corresponding chamber towards the corresponding opening (36).

The device may additionally comprise: a rotary actuator configured to rotate the rotor (119, 219) relative to the technical axis (120, 220); moreover, the rotary actuator contains: the first guide means (52) located on the rotor (119, 219); and a second guide means (50) located on the casing (112); wherein the first guiding means (52) is configured to interact with the second guiding means (50) for rotating the rotor (119, 219) about the technical axis (120, 220).

At least one of the first guide means (52) and the second guide means (50) may include an electromagnet configured to magnetically couple with another of the first guide means (52) and the second guide means (50).

The device may additionally comprise: a rotary actuator configured to rotate the rotor (119, 219) relative to the technical axis (120, 220); moreover, the rotary actuator contains: the first guide means (52) on the rotor (119, 219); and a second guide means (50) on the shroud (112); the first guide means (52) complements the second guide means (50) in shape; wherein one of the first and second guide means forms a path (50) along which the other of the first and second guide means (52) is forced to follow; wherein the other of the first and second guide means (52) comprises a rotatable element (820) configured to engage with the tract (50) and rotate as it moves along the tract (50).

The heat source may further comprise a substance passing through a channel (303) in the first heat exchanger 302a, while the device (1000) provides cooling of the substance.

The fluid passing through the device may contain air.

In some examples, the device comprises a motor (308) coupled to the first shaft portion 118 to drive the rotor (119) about the first rotation axis (130).

The motor (308) can be reversible so that when the motor can drive the rotor (119) about the first axis of rotation (130) in the first direction, the first heat exchanger (302a) can function as a heat source to transfer heat from the specified substance to the fluid. wherein when the motor can drive the rotor (119) about the first axis (130) of rotation in a second direction opposite to the first direction, the first heat exchanger (302a) can function as a heat sink to transfer heat from the fluid to the specified substance.

The second guide means (550) may comprise a pivot ring (527) adapted to support at least a part of the bearing (529) connected to the casing on it.

The first guide means (552) may include a pin adapted to receive a pivot ring (527).

In one embodiment, a rotational thermodynamic device (100) with a first flow portion (111) is provided, comprising: a first shaft portion (118) defining a first rotation axis (130) and rotatable around it; a first technical axis (120) defining a second axis of rotation (132), the first shaft portion (118) passing through the first technical axis (120); a first piston element (122a) located on a first shaft portion (118), the first piston element (122a) extending from the first technical axis (120) towards the distal end of the first shaft portion (118); the first rotor (119) carried by the first technical axle (120); wherein the first rotor (119) comprises: a first chamber (134a), wherein the first piston element (122a) passes through the first chamber (134a); a first casing wall adjacent to the first chamber (134a), a first window (114a) and a second window (114b) located in the casing wall, each in fluid communication with the first chamber (134a); whereby: the first rotor (119) and the first technical axis (120) are made with the possibility of rotation with the first shaft part (118) around the first axis (130) of rotation; wherein the first rotor (119) is rotatable relative to the technical axis (120) around the second axis (132) of rotation to provide the first rotor (119) with the possibility of rotation relative to the first piston element (122a) when the first rotor (119) rotates around the first axis (130) rotation; whereby the first flow path (111) is configured to allow fluid to pass from the first port (114a) to the second port (114b) through the first chamber (134a); the device further comprises a second flow part (115) comprising: a second chamber (134b, 234b), a second piston element (122b) extending from the other side of the first technical axis (120) along the first shaft part (118); the second piston element (122b) passes through the second chamber (134b); to provide the first rotor (119) with the possibility of rotation relative to the second piston element (122b) when the first rotor (119) rotates around the first axis (130) of rotation, the second wall of the casing adjacent to the second chamber (134b, 234b), the third window (116a) and a fourth window (116b) located in the second wall of the casing, each of them in fluid communication with the second chamber (134b, 234b), whereby the second flow path (115) is configured to allow fluid to pass from the third window (116a) to the fourth window (116b) through the second chamber (134, 234b); wherein the first flow path (111) and the second flow path (115) are two sides of the first rotor (119), one of the first flow path (111) and the second flow path (115) being configured to function as a compressor, and the other of the first flow path (111) and the second flow path (115) are configured to function as an expander, with the second port (114b) in fluid communication with the third port (116a) through the first heat exchanger (302a).

Thus, a device capable of displacing and expanding a fluid can be created, which can be configured as a heat pump to extract heat from a system (for example, a refrigeration device) or as a heat engine to create rotation at the outlet due to the work of the working fluid. ...

The displacement part (for example, a pump) and the expansion part (for example, a turbine) of the proposed device can maintain their optimal efficiency at almost identical rotational speeds, while, due to the fact that they are located within the same device, a single set of mechanical restrictions. Thus, the configurations of the present disclosure may be substantially thermodynamically ideal.

The device may comprise a core element with associated displacement and expansion chambers bounded by the walls of a single common rotor. The rotor is rotatable relative to the rotatable piston element. As a result, this configuration forms a positive displacement system capable of efficiently operating at speeds lower than those of prior art devices. The system is also designed to operate at speeds not lower than in the examples of known devices.

The core elements can be characterized by the word "roticulator", since the rotor according to the present disclosure is made with the possibility of simultaneous rotation (English "rotate") and rotation in the joint (English "articulate"), for example, as disclosed in PCT Application PCT / GB2016 / 052429 (published as WO 2017/089740). Thus, there is provided a heat engine or heat pump including a "rotational device".

"Rotation" or the concept "rotational" means that in the device one and the same body (for example, the rotor) rotates with simultaneous rotation in the joint, that is, movement in three-dimensional space, due to which it is possible to perform voluminous "work" in the joint and movement with rotation.

Due to this, the device provides the possibility of absolute control and regulation of several volumetric chambers with mechanical restrictions / losses of the same order. Given the high volumetric change and the magnitude of mechanical losses, this device, in comparison with conventional devices, has a high efficiency factor.

Considering the above, the disclosed device is made with the possibility of both volumetric displacement and creating an absolute vacuum in its working volumes, which is typical for an "ideal" expander / compressor / pump, and provides a high expansion / compression ratio, much higher than that created by known devices.

The device satisfies an ongoing need for a single device capable of both expanding a working fluid and compressing and / or displacing the same working fluid.

The heat engine of the present disclosure can operate with lower temperature differentials and lower quality heat than prior art examples.

Since the first flow path and the second flow path (e.g., the expansion and displacement portions) are connected, the heat pump of the present disclosure is inherently more efficient than any example of a prior art device because fluid expansion is used to drive the drive / pump. / compression part, thereby reducing the need for external input power from the motor.

Thus, the device of the present disclosure can operate effectively under a wide range of conditions, allowing it to produce results under input conditions such that there would not be sufficient power to operate examples of prior art devices.

Brief Description of Drawings

Next, the device according to the present disclosure will be described using examples of the accompanying drawings, where:

FIG. 1 is a partial exploded view of an example of an apparatus including a rotor assembly and a casing according to the present disclosure;

FIG. 2 is an outside perspective view of a device according to the present disclosure with a different casing and windows than those shown in FIG. one;

FIG. 3 is a "translucent" perspective view of the device of FIG. 1 complete;

FIG. 4 shows in more detail the rotor assembly of FIG. one;

FIG. 5 shows the rotor of the rotor assembly of FIG. 4;

FIG. 6 is an end view of the rotor assembly of FIG. 4;

FIG. 7 is an end view of the rotor of FIG. five;

FIG. 8 is an isometric view of the technical axis of the rotor assembly;

FIG. 9 is an isometric view of the shaft of the rotor assembly;

FIG. 10 shows the technical axis in FIG. 8 assembled with the shaft of FIG. nine;

FIG. 11 is a plan view of the casing of FIG. 1, in which the hidden node is indicated by dotted lines;

FIG. 12 is an inside view of the casing of FIG. eleven;

FIG. 13 is an inside view of the rotor casing of FIG. 2;

FIG. 14 depicts an alternative example of a rotor;

FIG. 15 depicts a first example of a closed loop heat pump according to the present disclosure suitable for a refrigeration device;

FIG. 16 depicts a second example of a closed loop heat pump according to the present disclosure suitable for a refrigeration device;

FIG. 17, 18 show alternative means for creating a difference in rotor volumes that could be included in the heat pumps of FIG. 15, 16, respectively, or in the composition of heat engines according to additional examples of the present disclosure;

FIG. 19 depicts a first example of a closed loop heat engine according to the present disclosure, suitable, inter alia, for an energy harvesting device;

FIG. 20 depicts a second example of a closed loop heat engine according to the present disclosure, suitable, inter alia, for an energy harvesting device;

FIG. 21 depicts a first example of an open loop heat engine according to the present disclosure, suitable, inter alia, for a power generating device;

FIG. 22 depicts a second example of an open loop heat engine according to the present disclosure, suitable, inter alia, for a power generating device;

FIG. 23 depicts a third example of an open loop heat engine according to the present disclosure, suitable, inter alia, for a power generating device;

FIG. 24 depicts a fourth example of an open loop heat engine according to the present disclosure, suitable, inter alia, for a power generating device;

FIG. 25 depicts an example of an open loop heat pump according to the present disclosure suitable for a refrigeration device;

FIG. 26 is an exploded view of an example of an alternative rotor assembly; and

FIG. 27A and 27B are side and cross-sectional views of the rotor assembly of FIG. 26.

Implementation of the invention

The device according to the present invention and its method of operation are disclosed below.

In particular, the present disclosure relates to a device constituting a "rotational" thermodynamic device capable of functioning as a heat pump and / or a heat engine.

In other words, the device is suitable for use in a hydraulic device capable of functioning as a heat pump and / or a heat engine. The core elements of the device are disclosed, as well as non-limiting examples of possible applications of the device.

The expression "fluid" should be understood in its usual meanings, for example: "liquid", "gas", "vapor", or "a combination of liquid, gas and / or vapor", or "a substance that behaves like a fluid."

FIG. 1 is a partial exploded view of the core 10 of the device according to the present disclosure. The features of the core 10 are disclosed in FIG. 1-14, 17, 18 and FIG. 15, 16 and 19-24 illustrate how core 10 is combined with other features to form the heat pump and / or heat engine of the present disclosure. The core comprises a casing 12 and a rotor assembly 14. FIG. 2 depicts an alternative example of the casing 12 as it encloses the rotor assembly 14.

In the example of FIG. 1, the casing 12 is divided into two parts 12a, 12b, enclosing the rotor assembly 14. In this alternative example, the casing can be made of more than two parts and / or divided in a different way than shown in FIG. one.

The rotor assembly 14 contains a rotor 16, a shaft 18, a technical axis (English axle) 20 and a piston element 22. The casing 12 contains a wall 24 defining the cavity 26, while the rotor 16 is rotatable and rotatable within the cavity 26.

The shaft 18 forms the first axis of rotation 30 and is rotatable about it. The technical axis 20 surrounds the shaft 18. The technical axis is at an angle to the shaft 18. The technical axis also forms the second axis of rotation 32. In other words, the technical axis 20 forms the second axis of rotation 32, and the shaft 18 passes through the technical axis 20 at an angle to the technical axis 20. The piston element 22 is located on the shaft 18.

In the examples disclosed, the device is configured with two piston elements 22, i. E. the first and second piston elements 22. The rotor 16 also forms two chambers 34a, b, diametrically opposed to each other on each side of the rotor 16.

In examples where the device is part of a fluid compression device, each chamber 34 may be a compression chamber. Likewise, in examples where the device is a fluid displacement device, each chamber 34 may be a displacement chamber. In examples where the device is a fluid expansion device, each chamber 34 may be an expansion or dosing chamber.

While the piston element 22 may actually be a single piece extending from one end to the other end of the rotor assembly 14, this configuration effectively means that each chamber 34 is provided with a piston element 22. In other words, although the piston element 22 can only consist of one part, it can form two sections 22 of the piston element, one on each side of the rotor assembly 14.

In other words, the first piston element 22 extends from one side of the technical axis 20 along the shaft 18 to one side of the housing 12, and the second piston element 22 extends from the other side of the technical axis 20 along the shaft 18 to the other side of the housing 12. The rotor 16 comprises a first chamber 34a with a first hole 36 on one side of the rotor unit 14 and a second chamber 34b with a second hole 36 on the other side of the rotor unit 14. The rotor 16 carries the technical axis 20, while the rotor 16 is rotatable about the technical axis 20 about the second axis 32 rotation. The piston element 22 extends from the technical axis 20 through the chambers 34a, b to the holes 36. A small gap is left between the edges of the piston element 22 and the rotor wall 16 defining the chamber 34. The gap may be small enough to create a seal between the edges of the piston element 22 and the rotor wall 16 defining chamber 34. Alternatively or additionally, sealing elements may be disposed between the piston members 22 and the rotor wall 16 defining chamber 34.

Chambers 34 are delimited by side walls (i.e., the ends of chambers 34) for movement towards and away from piston elements 22, the side walls being connected by boundary walls that can be moved past the sides of piston element 22. In other words, chambers 34 are delimited side walls / ends and boundary walls located in the rotor 16.

Thus, the rotor 16 is made with the possibility of rotation with the shaft 18 about the first axis of rotation 30 and rotation about the technical axis 20 about the second axis of rotation 32. By this configuration, the first piston member 22 is movable (i.e., movable) from one side of the first chamber 34a to the opposite side of the first chamber 34a as the rotor 16 rotates about the first axis of rotation 30. In other words, since the rotor 16 is rotatable with the shaft 18 about the first axis of rotation 30 and is rotatable about the technical axis 20 about the second axis of rotation 32, during operation there is a rotary (i.e. rocking) movement of the rotor 16 relative to the first piston element 22 when the rotor 16 rotates about the first axis of rotation 30. In other words, the device is made with the possibility of controlled rotary movement of the rotor 16 relative to the first piston element 22 when the rotor 16 rotates around the first axis of rotation 30.

In addition, due to this configuration, the second piston member 22 is movable (i.e., movable) from one side of the second chamber 34b to the opposite side of the second chamber 34b as the rotor 16 rotates about the first axis of rotation 30. In other words, since the rotor 16 is rotatable with the shaft 18 about the first axis of rotation 30 and is rotatable relative to the technical axis 20 about the second axis of rotation 32, during operation there is a rotary (i.e. rocking) movement of the rotor 16 relative to both piston elements 22 when the rotor 16 rotates about the first axis of rotation 30. In other words, the device is made with the possibility of controlled rotary movement of the rotor 16 relative to both piston elements 22 when the rotor 16 rotates around the first axis of rotation 30.

The relative pivotal movement occurs under the action of a pivot actuator, as disclosed below.

The fact that the rotor 16 is mounted with the possibility of rotation (i.e. rocking) relative to the piston elements 22 means that the piston elements 22 can create a movable barrier between the two halves of the chamber 34a, b or each of them with the formation of subchambers 34a1, 34a2, 34b1, 34b2 in cells 34a, 34b. During operation, the volume of each subchamber 34a1, 34a2, 34b1 and 34b2 changes depending on the relative orientation of the rotor 16 and the piston elements 22.

When the shroud 12 encompasses the rotor assembly 14, the rotor 16 is positioned relative to the shroud wall 24 to maintain a small gap between the chamber opening 34 against most of the wall 24. The gap may be small enough to create a seal between the rotor 16 and the shroud wall 24.

Alternatively or additionally, sealing elements may be located in the gap between the casing wall 24 and the rotor 16.

Windows can be created to transfer fluid to and from chambers 34a, b. For each chamber 34, enclosure 12 may include an inlet 40 for supplying fluid to chamber 34 and an outlet / outlet 42 for removing fluid from chamber 34. Windows 40, 42 extend through the enclosure and open onto wall 24 of enclosure 12.

FIG. 1 and FIG. 2 shows the different orientations of the inlet and outlet / outlet ports 40, 42. FIG. 1, the direction of flow formed by each of the windows is directed at an angle to the first axis of rotation 30. FIG. 2, the direction of flow formed by each of the windows is parallel to the first axis of rotation 30. The passage section of the windows 40, 42 can be the same. In other examples, the flow areas of the windows 40, 42 may be different from each other.

A bearing assembly 44 can also be provided to support the ends of the shaft 18. It can be of any known type suitable for a given application.

The windows 40, 42 can be sized and located on the casing 12 so that during operation, when the corresponding openings 36 of the chambers move past the windows 40, 42, in the first relative position the openings 36 are coaxial with the windows 40, 42, whereby the openings of the chambers completely open, while in the second relative position the holes 36 are misaligned with them, in connection with which the holes 36 are completely closed by the wall 24 of the casing 12, and in the intermediate relative position the holes 36 are partially coaxial with the windows 40, 42, in connection with which the holes 36 are partially narrowed by the wall 24 covers.

Alternatively, the windows 40, 42 can be sized and positioned on the casing 12 so that, during operation, in a first range (or set) of relative positions of the windows 40, 42 and the respective rotor openings 36, the windows 40, 42 and the openings 36 of the rotor are misaligned, and therefore the holes 36 are completely covered by the wall 24 of the casing 12 to block the flow of fluid between the subchambers 34a1, 34a2 and the corresponding window (s) 40,42 and block the flow of fluid between the subchambers 34b1, 34b2 and the corresponding window (s ) 40, 42. In the second range (or set) of relative positions of the windows 40, 42 and the corresponding openings 36 of the rotor chambers, the openings 36 are at least partially coaxial with the windows 40, 42, in connection with which the openings 36 are at least partially open to pass the flow of fluid between the subchambers of the chamber (s) 34a, b and the corresponding window (s). Thus, the subchambers are made with the possibility of increasing in volume, at least when they are fluidly connected to the inlet window (for passing the fluid flow into the subchamber), while the subchambers are made with the possibility of decreasing in volume at least when they are in fluid communication with the outlet window (to pass the fluid flow from the subchamber).

The location and size of the windows can be dependent on the application (i.e., whether they are included in a fluid pump device, a fluid displacement device, a fluid expansion device) to provide the highest operational efficiency. The locations of the windows disclosed in this description and depicted in the figures serve solely to indicate the principle of entry and exit of a medium (eg, a fluid).

In some examples of the devices of the present disclosure (not shown), inlet ports and outlet ports may be provided with mechanical or electromechanical valves configured to control the flow of fluid / media through ports 40, 42.

The device may include a rotary actuator. A non-limiting example of a rotary actuator is illustrated in FIG. 3 and corresponds to the device in FIG. 12.

In this case, the rotary actuator can comprise guiding means in any form suitable for controlling the rotary movement of the rotor. For example, the rotary actuator may include an electromagnetic assembly configured to control the rotary motion of the rotor. In other words, the rotary actuator may comprise a first guide means 52 located on the rotor 119, 219 and a second guide means 50 located on the casing 112, the first guide means 52 being adapted to cooperate with the second guide means 50 to rotate the rotor about technical axis. At least one of the first guide means 52 and the second guide means 50 comprises an electromagnet configured to be magnetically coupled with another of the first guide means 52 and the second guide means 50.

In whatever form, the rotary actuator is configured to rotate the rotor 16 about the technical axis 20. In other words, the device may further comprise a rotary actuator configured to rotate the rotor 16 about the second axis of rotation 32 formed by technical axis 20. The rotary actuator can be configured to rotate the rotor 16 at any angle suitable to ensure the desired performance of the device. For example, the rotary actuator may be configured to rotate the rotor 16 substantially about 60 degrees.

The rotary actuator may comprise, as disclosed in the examples, a first guiding means on the rotor 16 and a second guiding means on the casing 12. Thus, the rotary actuator can be configured as a mechanical link between the rotor 16 and the casing 12 to drive the rotor 16 into a controlled a relative pivotal movement relative to the piston element 22 when the rotor 16 rotates about the first axis of rotation 30. In other words, it is the relative movement of the rotor 16, which overcomes the force of the guiding means of the rotary actuator, that generates the rotary movement of the rotor 16.

The first guide means complements the second guide means in shape. One of the first and second guide means forms a path along which the other of the first and second guide means is forced to follow when the rotor rotates about the first axis of rotation 30. This path, which can be a groove, has a trajectory configured to induce the rotor 16 to rotate about the technical axis 20 and the axis 32. This trajectory also provides a power gain between the rotation and rotation of the rotor 16.

As disclosed in the example in FIG. 1 and more evident in FIG. 4, the pin 52 is located on the rotor 16, and, as shown in FIG. 1, 3, the guide groove 50 is located in the casing 12. In other words, the guiding path 50 can be located on the casing, and another guide means, the pin 52, can be located on the rotor 16.

A rotor assembly 14 similar to the example in FIG. 1, 3 is disclosed in FIG. 4-7. From this example, it can be seen that the pin 52 is located on the rotor 16 with the ability to engage with the guide groove 50 on the casing 12.

The rotor 16 can be substantially spherical. It is shown that the rotor 16 can be at least partially substantially spherical. For convenience, FIG. 4 shows a complete rotor assembly 14 with installed shaft 18, technical axis 20 and piston element 22. In this case, FIG. 5 depicts the rotor 16 itself and a cavity 60 extending through the rotor 14 and adapted to receive a technical shaft 20. FIG. 6 is a view along the first axis of rotation 30 in FIG. 6, and FIG. 7 is the same view as in FIG. 6, but looking down into the opening 36 defining the chamber 34 of the rotor 14.

FIG. 8 is an isometric view of the technical shaft 20 with a passage 62 for receiving the technical shaft 18 and piston member 22. The technical shaft 20 is substantially cylindrical. FIG. 9 shows an example of the configuration of the shaft 18 and the piston element 22. The shaft 18 and the piston element 22 can be made in one piece, as in FIG. 10, or made of several parts. The piston member 22 is substantially square or rectangular in cross section. The figures show that the shaft 18 may include cylindrical bearing regions extending from the piston member 22 for positioning on the bearing assembly 44 of the housing 12 and thereby allowing the shaft 18 to rotate about the first axis of rotation 30.

FIG. 10 shows a shaft 18 and piston element 22 assembled with a technical shaft 20. They can be formed as an assembly as described above, or be made in one piece, such as cast or forged.

The technical axis 20 may be located substantially at the center of the shaft 18 and the piston member 22. In other words, the technical axis 20 may be located substantially halfway between the two ends of the shaft 18. When assembled, the shaft 18, the technical axis 20 and the piston member 22 can be motionless relative to each other. The technical axis 20 may be substantially perpendicular to the shaft and piston member 22, and thus the second axis of rotation 32 may be substantially perpendicular to the first axis of rotation 30.

The piston elements 22 are sized to fit their ends close to the wall 24 of the casing 12, leaving a small gap between the ends of the piston elements 22 and the wall 24 of the casing. The gap can be small enough to create a seal between the piston members 22 and the housing wall 24. Alternatively or additionally, sealing elements may be disposed in the gap between the housing wall 24 and the piston members 22.

Additional examples of guide groove 50 are shown in cross-section in FIG. 11, 12 corresponding to the example in FIG. 1. In this example, the guide groove 50 is substantially circular (ie, no kinks).

The rotor 14 may be one or more pieces assembled around the shaft assembly 18 and the technical axis 20. Alternatively, the rotor 16 may be a single piece formed in one piece or made from several pieces to form a single piece. , in this case, the technical axis 20 can be pushed into the cavity 60, after which the shaft 18 and the piston element 22 can be pushed into the passage 62 formed in the technical axis 20 and then attached to each other. A small gap may be left between the technical shaft 20 and the shaft of the rotor cavity 60 16. The clearance may be small enough to create a seal between the technical shaft 20 and the rotor shaft 16 in the cavity 60. Alternatively or additionally, in the clearance between the technical shaft 20 and the rotor barrel 16 the cavity 60 may contain sealing elements.

From FIG. 13, it is obvious that, in the example where the guiding means is formed as a path on the casing 12, the guiding path 50 forms a path around the first circumference of the casing (i.e., on, near and / or on one side of it). In this example, the plane of the first circle finds itself on the plane formed by the second axis of rotation 32, or coaxial to it, while rotating about the first axis of rotation 30.

FIG. 13 shows a half of the casing, separated in a horizontal plane, on which the first axis of rotation 30 is located. The guide path 50 contains at least the first point of inflection 70 (on one side of the casing 12) for changing the direction of the path from the first side of the plane of the second axis of rotation 32, then to the second side of the plane of the second axis of rotation 32, and a second point of inflection 72 (on the opposite side of the casing) to change the direction of the path 50 from the second side of the plane of the second axis of rotation 32, and then back to the first side of the plane of the second axis of rotation 32. Thus, the path 50 is not coaxial with the plane of the second axis of rotation 32, but passes from one side to the other side of the plane of the second axis of rotation 32. In other words, the path 50 is not located on the plane of the second axis of rotation 32, but forms a sinusoidal path between different sides of the plane of the second axis of rotation 32. The path 50 can be offset from the second axis of rotation 32. Therefore, when the rotor 16 rotates about the first axis of rotation 30, the interaction of the path 50 and the pin 52 causes the rotor 16 to tilt (i.e. swing or rotate) back and forth about the technical axis 20 and, therefore, the second axis of rotation 32.

In such an example, the distance that the guide path extends from the bend 70, 72 on one side of the plane of the second axis of rotation 32 to the bend 70, 72 on the other side of the plane of the second axis of rotation 32 determines the relationship between the angle of rotation of the rotor 16 about the second axis of rotation 32 and the angle of rotation of the shaft 18 about the first axis of rotation 30. The number of bends 70, 72 determines the ratio of the number of rotations (eg, cycles of compression, expansion, displacement, etc.) of the rotor 16 about the second axis of rotation 32 per revolution of the rotor 16 about the first axis of rotation 30.

In other words, the directionality of the guide path 50 determines the linear change, the amplitude and the frequency of turns of the rotor 16 about the second axis of rotation 32 in relation to rotation about the first axis of rotation 30, thereby determining the ratio of the angle of displacement of the chambers 34 to the radial movement by means of the shaft (or vice versa) in any point.

In other words, the orientation of the path 50 directly determines the mechanical ratio / relationship between the circumferential speed of the rotor and the rate of change in the volume of the chambers 34a, 34b of the rotor. In other words, the trajectory of the path 50 directly determines the mechanical ratio / relationship between the peripheral speed of the rotor 16 and the speed of rotation of the rotor 16. Thus, the ratio of the rate of change in the volume of the chambers and the magnitude of their displacement and the peripheral speed of the rotor unit 14 depends on the sharpness of the change in the trajectory (i.e. bend) of the guide path.

The groove profile can be adjusted to achieve a variety of combinations of displacement and compression characteristics, since combustion engines fueled by gasoline, diesel (or other fuels) may require different characteristics and / or adjustments during the life of the rotor assembly for pumping and expansion. ... In other words, the trajectory of the path 50 can be changed.

Thus, the guide path 50 forms a "programmable crank path" that can be predefined for any application of the device. In other words, the trajectory can be optimized for the needs of this application. In other words, the guide path can be programmed for different applications.

Alternatively, the means forming the guide path 50 may be movable to allow the path 50 to be adjusted and thereby dynamically adjust the crank path during operation of the device. This makes it possible to control the speed and the magnitude of the rotary action of the rotor around the second axis of rotation to facilitate regulation of the performance and / or efficiency of the device. In other words, the adjustable crank path allows for a change in the mechanical ratio / relationship between the peripheral speed of the rotor and the rate of change or the amount of displacement of the volume of the rotor chambers 34a, 34b. Thus, the path 50 can be made in the form of a slot element or the like attached to the rotor 12 and rotor case 16 so that it can be moved and / or adjusted, in part or in whole, relative to the rotor 12 and rotor case 16.

Thus, the path 50 and kinks 70, 72 determine the rate of change in the displacement of the rotor 16 relative to the piston element 22, allowing the mechanical gain between rotation and rotation of the rotor 16 to be significantly influenced.

FIG. 14 depicts another non-limiting example of a rotor 16 similar to those disclosed in FIG. 4-7. Areas 73 for bearing are shown to accommodate a bearing assembly (e.g., a roller bearing assembly) or to create a bearing surface for the rotor 16 on the technical axis 20. Also shown is a "cutout" 74 made as a cavity in an irrelevant area of the rotor, which facilitates construction (i.e. e. provides an advantage in terms of weight reduction) and forms an area for gripping / securing / supporting the rotor 16 during manufacture. An additional area 75 may also be provided in the immediate vicinity of the pin 52 for gripping / securing / supporting the rotor 16 during manufacture. In this example, pin 52 is a roller bearing rotatable about an axis perpendicular to axis 32. The bearing engages and moves along the guide path 50 while rotating along the track to minimize friction between the guide and track elements.

FIG. 15, 16 and 19-24 illustrate how the rotor device of FIG. 1-14, 17, 18 can be adapted to function as a heat pump or heat engine. Any of the features disclosed in the examples of FIG. 1-14, 17, 18 may be included in the configuration of FIG. 15, 16 and 19-24. General terms have been used to refer to common features, however, in order to distinguish features from different examples from each other, corresponding alternative reference numbers have been used.

EXAMPLE 1 - SINGLE UNIT, CLOSED CIRCUIT, HEAT PUMP

FIG. 15 illustrates an apparatus 100 according to the present disclosure in the form of a closed loop heat pump such as a refrigeration unit.

As disclosed in the example of FIG. 1-14, device 100 includes a first shaft portion 118 (similar to shaft 18) defining and rotatable about a first axis of rotation 130 (similar to axis 30 of rotation). The first technical axis 120 (similar to the technical axis 20) defines a second axis of rotation 132 (similar to the axis of rotation 32), with the first shaft portion 118 passing through the first technical axis 120. The second axis 132 of rotation is substantially perpendicular to the first axis of rotation 130. The first piston element 122a (similar to the first piston element 22) is located on the first shaft portion 118, with the first piston element 122a extending from the first technical axis 120 towards the distal end of the first shaft portion 118. The first rotor 119 (similar to the rotor 16 in FIG. 1) -14, 17, 18) carries the first service axle 120. A shroud 112 (similar to shroud 12) is located around the rotor assembly 119.

The first rotor 119 includes a first chamber 134a (similar to the first chamber 34a), with the first piston member 122a passing through the first chamber 134a. The wall of the casing 112 is disposed adjacent to the first chamber 134a.

In the wall of the casing 112 and adjacent to the first chamber 134a, a first window 114a and a second window 114b (i.e., similar to windows 40, 42) are located. Windows 114a, 114b are in fluid communication with the first chamber 134a and are configured to function as flow inlets / outlets.

The first chamber 134a is divided into subchambers 134a1, 134a2 (similar to subchambers 34a1, 34a2) on opposite sides of the first piston element 122a. Therefore, at any time, windows 114a, 114b can be connected downstream with one of the subcameras 134a1, 134a2, but not both.

The first rotor 119 includes a second chamber 134b (similar to the second chamber 34b). The wall of the casing 112 is adjacent to the second chamber 134b. The housing 112 includes a third port 116a and a fourth port 116b in fluid communication with the second chamber 134b. Windows 116a, 116b are in fluid communication with the first chamber 134b and are configured to function as flow inlets / outlets.

The second chamber 134b is divided into subchambers 134b1, 134b2 (similar to subchambers 34b1, 34b2) on opposite sides of the second piston member 122b. Therefore, at any time, windows 116a, 116b may be downstream of one of the subcameras 134b1, 134b2, but not both.

The first piston element 122a extends from one side of the first technical axis 120 along the first shaft portion 118, and the second piston element 122b (similar to the second piston element 22) extends from the other side of the first technical axis 120 along the first shaft 118, through the second chamber 134b. Thus, as disclosed in the examples of FIGS. 1-14, this configuration allows the first rotor 119 to rotate relative to the second piston member 122b as the first rotor 119 rotates about the first axis 130 of rotation.

The first shaft portion 118, the first technical shaft 120, and the first piston element (s) 122a may be stationary relative to each other.

Thus, the first rotor 119 and the first technical axis 120 are rotatable with the first shaft portion 118 about the first rotational axis 130, while the first rotor 119 is rotatable about the technical axis 120 about the second rotational axis 132 to allow the first the rotor 119 relative to the first piston member 122a as the first rotor 119 rotates about the first axis of rotation 130.

The second port 114b is in fluid communication with the third port 116a through a first conduit 300a containing a first heat exchanger 302a. The first heat exchanger 302a is configured to extract thermal energy from the working fluid passing through it. In other words, the first heat exchanger 302a is a heat sink for the working fluid (i.e., a heat sink for the fluid or media flowing through the system). The first section 300a1 of the duct 300a connects the second window 114b to the first heat exchanger 302a, and the second section 300a2 of the duct 300a connects the first heat exchanger 302a to the third window 116a. In other words, the fluid in the channel 300a can pass through the first heat exchanger 302.

Thus, the first chamber 134a, the heat exchanger 302a, and the second chamber 134b are located in series downstream.

The fourth port 116b is in fluid communication with the first port 114a through a second conduit 304a including a second heat exchanger 306a. The second heat exchanger 306a is configured to transfer thermal energy to a working fluid passing through it. In other words, the second heat exchanger 306a is a heat source for the working fluid (i.e., a heat source for the fluid or media flowing through the system).

The first heat exchanger 302a can be any suitable heat sink (eg, thermally associated with the volume to be heated, river, ambient air, etc.). The second heat exchanger 306a may include or be thermally associated with any suitable heat source (eg, volume to be cooled, interior air in a grocery store, etc.).

The first section 304a1 of the duct 304a connects the fourth window 116b to the second heat exchanger 306a, and the second section 304a2 of the duct 304a connects the second heat exchanger 306a to the first window 114a.

A motor 308 is coupled to a first shaft portion 118 to rotate the rotor 119 about a first axis of rotation 130.

In this example, the first chamber 134a and the first piston element 122a define the first flow portion 111, in this example configured to function as a compressor or displacement pump. Thus, the first flow portion 111 is configured to allow fluid to pass from the first port 114a to the second port 114b through the first chamber 134a.

In addition, the second chamber 134b and the second piston member 122b form a second flow portion 115, in this example configured to function as a metering portion or expansion portion. Thus, the second flow portion 115 is configured to allow fluid to pass from the third port 116a to the fourth port 116b through the second chamber 134.

The volumetric capacity of the second chamber 134b of the first rotor may be substantially equal to, less than or greater than, the volumetric capacity of the first chamber 134a of the first rotor.

In other words, in this example, the volumetric capacity of the second flow portion 115 may be equal to the volumetric capacity of the first flow portion 111, be less or greater than it.

For example, the volumetric capacity of the second chamber 134b of the first rotor may be no more than half the volumetric capacity of the first chamber 134a of the first rotor.

Alternatively, the volumetric capacity of the second chamber 134b of the first rotor may be at least twice the volumetric capacity of the first chamber 134a of the first rotor.

In this example, this provides some degree of expansion within a single device (eg, disclosed in FIG. 17).

This can be achieved by making the first chamber 134a of the first rotor different in width from the second chamber 134b of the first rotor, whereby, as a consequence, the width of the first piston element 122a is different from the width of the second piston element 122b. Therefore, although the piston members rotate and thus move by the same amount about the second axis of rotation 132, the volume of the chambers 134a, 134b and the working volume of the first and second piston members 122a, 122b will be different from each other.

As disclosed in FIG. 17, showing only the rotor assembly 116, different volumes can be achieved by making the first chamber 134a of the first rotor wider than the second chamber 134b of the first rotor, whereby the width of the first piston element 122a is greater than the width of the second piston element 122b. Therefore, although the piston elements will rotate and thus move by the same amount about the second axis of rotation 132, the volume of the chamber 134a will be greater than the volume of the chamber 134b and, thus, the working volume of the first piston element 122a will be greater than at the second piston element 122b.

During operation (as disclosed below), a working fluid is introduced into the system and circulated through it.

The fluid can be a refrigerant fluid or other medium, such as, but not limited to, ethanol, R22, or supersaturated CO ₂ .

Given that the system is essentially closed, there may be no depletion of working fluid or loss of serviceability after each cycle. In other words, during most of the service life, the same constant volume of working fluid will be maintained and will constantly circulate through the system. In alternative examples, partial or complete replacement of the working fluid is possible during operation of the device (eg, every cycle or after a predetermined number of cycles).

Since the first flow path 111 (in this example, the displacement / compressor / pump portion) and the second flow path 115 (in this example, the metering / expansion portion) are two sides of the same rotor, the rotor 119 drives both the motor and dosing / expanding the fluid in the second chamber 134b (i.e., in the subchambers 134b1, 134b2). Thus, this configuration of the device of the present disclosure allows some energy to be drawn from the expansion stage to partially drive the rotor 119.

The operation of the device 100 will be disclosed below.

Stage 1

In the example of FIG. 15, the working fluid enters the subchamber 134a1 through the window 114a.

Next, the working fluid is pumped (for example, compression) under the action of the first piston element 122a, driven by the motor 308, in the sub-chamber 134a and its exit through the second window 114b.

Simultaneously with the withdrawal of the working fluid into the subchamber 134a1, the working fluid is discharged from the subchamber 134a2 through the second window 114b.

Simultaneously with the discharge of the working fluid from the subchamber 134a1, the working fluid is taken into the subchamber 134a2 through the first window 114b.

Stage 2

In the example of FIG. 15, after being discharged from the first chamber 134a of the rotor 119, the working fluid flows through the passage 300a1 and enters the first heat exchanger 302a, which is configured as a heat sink. Therefore, heat is removed from the working fluid as it passes through the first heat exchanger 302a.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the first heat exchanger 302a.

Stage 3

In the example of FIG. 15, the working fluid passes through the channel 300a2 and enters the rotor subchamber 134b1 through the third port 116a, where its pressure is limited, and the working fluid is metered into the channel 304a through the fourth port 116b.

Simultaneously with the entry of the working fluid into the subchamber 134b1, the working fluid is discharged from the subchamber 134b2 through the fourth port 116b.

As the rotor 119 continues to rotate, the working fluid is released from the subchamber 134b1 through the fourth port 116b, and more of the working fluid enters the subchamber 134b2 through the third port 116a, where it expands.

In all examples, the successive expansion of the working fluid in the rotor subchambers 134b1, 134b2 creates a force that (at least partially) rotates the rotor about its second axis of rotation and rotates the rotor about its first axis of rotation. This force is in addition to the force generated by the 308 motor.

Stage 4

In the example of FIG. 15, the working fluid then flows from the second chamber 134b through the channel 304a1 and enters the second heat exchanger 306a, in this example configured as a heat source.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the second heat exchanger 306a.

Thus, the working fluid absorbs heat from the heat source and then leaves the second heat exchanger 306a and passes through the conduit 304a2 before entering the first chamber 134a to start a new cycle.

EXAMPLE 2 - DUAL UNIT, CLOSED CIRCUIT, HEAT PUMP

FIG. 16 illustrates another example of a closed loop heat pump such as a refrigeration plant. This example contains many features that are common or equivalent to those of the example in FIG. 15, whereby the same reference numbers are used.

The device 200 comprises a first flow portion 111 which, as in the example of FIG. 15 can be configured to function as a compressor or displacement pump. The first flow portion 111 comprises a first port 114a and a second port 114b configured to function as flow inlets / outlets.

It also contains a second flow path 115 which, as in the example in FIG. 15 can be configured to function as a dispensing part or an expansion part. The second flow portion 115 includes a third port 116a and a fourth port 116b configured to function as flow inlets / outlets.

The device 200 includes a first shaft portion 118 defining and rotatable about a first axis of rotation 130. The first technical axis 120 defines a second axis of rotation 132, with the first shaft portion 118 extending through the first technical axis 120. The second axis of rotation 132 is substantially perpendicular to the first axis of rotation 130. The first piston element 122a is located on the first shaft portion 118, with the first piston element 122a extending from the first technical axis 120 towards the distal end of the first shaft part 118. The first rotor 119 carries the first technical shaft 120. The first rotor 119 comprises a first chamber 134a with the first piston member 122a extending through the first chamber 134a. The first displacement outlet 113a and the first displacement inlet 114a are in fluid communication with the first chamber 134a.

The first shaft portion 118, the first technical shaft 120, and the first piston element (s) 122a may be stationary relative to each other.

The first rotor 119 also includes a second chamber 134b. The first piston element 122a extends from one side of the first technical axis 120 along the first shaft 118 through the first chamber 134a to form subchambers 134a1, 134a2, and the second piston element 122b extends from the other side of the first technical axis 120 along the first shaft 118, through the second chamber 134b to form subchambers 134b1, 134b2. Therefore, this configuration allows the first rotor 119 to rotate relative to the second piston member 122b while the first rotor 119 rotates about the first rotational axis 130.

Thus, as disclosed in the examples in FIG. 1-14, the first rotor 119 and the first technical axis 120 are rotatable with the first shaft portion 118 about the first rotational axis 130, wherein the first rotor 119 is rotatable about the technical axis 120 about the second rotational axis 132 to allow rotational movement the first rotor 119 relative to the second piston member 122b as the first rotor 119 rotates about the first axis of rotation 130.

The device 200 further comprises a second shaft portion 218 rotatable about a first axis of rotation 130 and coupled to a first shaft portion 118 to rotate a first shaft portion 118 together with a second shaft portion 218 about a first axis of rotation 130.

The second technical axis 220 forms a third axis of rotation 232, with the second shaft portion 218 passing through the second technical axis 220. The third axis of rotation 232 is substantially perpendicular to the first axis of rotation 130 and is parallel to the second axis of rotation 132 of the first rotor, so it would extend beyond / inside the sheet as shown in FIG. sixteen.

The second rotor 219 carries the second technical shaft 220. The first shaft portion 118 is directly coupled to the second shaft portion 218, whereby the first rotor 119 and the second rotor are only rotatable at the same frequency. A second casing 212 (similar to casing 12) surrounds the second rotor 219.

Like the first rotor 119, the second rotor 219 includes a first chamber 234a and a second chamber 234b. The second piston element 222b is located on the second shaft portion 218, with the second piston element 222b extending from the second technical axis 220 through the second chamber 234b towards the distal end of the second shaft part 218 to form subchambers 234b1, 234b2.

The second piston element 222b extends from one side of the second technical axis 220 along the second shaft portion 218. The first piston element of the second rotor 222a extends from the other side of the second technical axis 220 along the second shaft part 218, through the first chamber 234a to form subchambers 234a1, 234a2. Thus, as disclosed in the examples in FIG. 1-14, this configuration is configured to allow the second rotor 219 to rotate relative to the first and second piston members 222a, 222b as the second rotor 219 rotates about the first axis of rotation 130.

The second shaft portion 218, the second technical shaft 220, and the second piston element (s) 222b may be stationary relative to each other.

In this example, the third window 116a and the fourth window 116b are in fluid communication with the second chamber 234b, with the third window 116a and the fourth window 116b being located in the wall of the second rotor casing 212.

Thus, the second rotor 219 and the second technical axis 220 are rotatable with the second shaft portion 218 about the first rotational axis 130, while the second rotor 219 is rotatable relative to the second technical axis 220 about the third rotational axis 232 to enable rotational movement the second rotor 219 relative to the first and second piston members 222a, 222b as the second rotor 219 rotates about the first axis of rotation 130.

The second port 114b of the first rotor 119 is in fluid communication with the third port 116a of the second rotor 219 through a first duct 300a containing the first heat exchanger 302a. As in the example in FIG. 15, the first heat exchanger 302a is configured to extract heat energy from the working fluid passing through it (i.e., it is a heat sink). The first section 300a1 of the duct 300a connects the second window 114b to the first heat exchanger 302a, and the second section 300a2 of the duct 300a connects the first heat exchanger 302a to the third window 116a.

The second chamber 134b of the first rotor is in fluid communication with the fifth port 114c and the sixth port 114d in the wall of the first casing 112, whereby this configuration allows fluid to pass from the fifth port 114c to the sixth port 114d through the second chamber 134b of the first rotor.

The first chamber 234a of the second rotor is in fluid communication with the seventh port 116c and the eighth port 116d in the wall of the second casing 212, whereby this configuration allows fluid to pass from the seventh port 116c to the eighth port 116d through the first chamber 234a of the second rotor.

The sixth port 114d of the first rotor 119 is in fluid communication with the seventh port 116c of the second rotor 219 through a second conduit 300b including (i.e., passing through) the first heat exchanger 302a. The first portion 300b1 of the duct 300b5 connects the sixth port 114d to the first heat exchanger 302a, and the second portion 300b2 of the duct 300b connects the first heat exchanger 302a to the seventh port 116c.

The fourth port 116b of the second rotor 219 is in fluid communication with the first port 114a of the first rotor 119 through a second conduit 304a including the second heat exchanger 306a. As in the example in FIG. 15, the second heat exchanger 306a is configured to transfer thermal energy to a working fluid passing therethrough (i.e., a heat source). The first section 304a1 of the duct 304a connects the fourth window 116b to the second heat exchanger 306a, and the second section 304a2 of the duct 300a connects the second heat exchanger 306a to the first window 114a.

The eighth port 116d of the second rotor 219 is in fluid communication with the fifth port 114 from the first rotor through a second conduit 304b including (ie, passing through) a second heat exchanger 306a. The first portion 304b1 of the duct 304b connects the eighth port 116d to the second heat exchanger 306a, and the second portion 304b2 of the duct 304b connects the second heat exchanger 306a to the fifth port 114c.

Thus, this example comprises two fluid circuits (e.g., between the first chamber 134a of the first rotor and the second chamber 234b of the second rotor, and also between the second chamber 134b of the first rotor and the first chamber 234a of the second rotor) that can be isolated from each other along fluid medium. The working fluid can be the same as in the example in FIG. fifteen.

In this example, the first rotor assembly 119 (i.e., the first rotor chambers 134a, 134b and the first and second piston elements 122a, 122b of the first rotor) and the first casing 112 form a first flow path 111, in this example configured to function as a compressor or a displacement pump. Thus, the first flow portion 111 is configured to allow fluid to pass from the first port 114a to the second port 114b through the first chamber 134a of the first rotor and to pass fluid from the fifth port 114c to the sixth port 114d through the second chamber 134b of the first rotor.

The rotor assembly 219 (i.e., the second rotor chambers 234a, 234b and the first and second piston elements 222a, 222b of the second rotor) and the second casing 212 form a second flow path 115, in this example configured to function as a metering portion or expansion portion ... Thus, the second flow portion 115 is configured to allow fluid to pass from the third port 116a to the fourth port 116b through the second chamber 234b of the second rotor and to pass fluid from the seventh port 116c to the eighth port 116d through the first chamber 234a of the second rotor.

As disclosed in FIG. 16, the first chamber 134a and the second chamber 134b of the first rotor 119 (i.e., the first flow portion 111) have substantially equal volumetric capacity. The first chamber 234a and the second chamber 234b of the second rotor 219 (i.e., the second flow path 115) have substantially equal volumetric capacity. In this case, the volumetric capacity of the chambers 134a, 134b of the first rotor (the first flow path 111) can be substantially equal to the volumetric capacity of the chambers 234a, 234b of the second rotor (the second flow path 115), be less or greater than it.

In other words, in this example, the volumetric capacity of the chambers 234a, 234b of the rotor of the second flow passage 115 can be equal to the volumetric capacity of the chambers 134a, 134b of the rotor of the first flow passage 111, be less or greater than it.

In other words, in this example, the volumetric capacity of the second flow portion 115 can be no more than half the volumetric capacity of the first flow portion 111.

Alternatively, in this example, the volumetric capacity of the second flow portion 115 may be at least twice the volumetric capacity of the first flow portion 111.

As disclosed in FIG. 18, showing only rotors 119, 219, the first and second piston elements 122, 222 and shafts 118, 218, the difference in volumetric capacity can be achieved by making the chambers 134a, 134b of the first rotor wider than chambers 234a, 234b of the second rotor, when the first and second piston members 122a, 122b of the first rotor will therefore be wider than the first and second piston members 222a, 222b of the second rotor. Therefore, although the first and second piston elements 122, 222 can rotate through the same angle, the volume of the first chambers 134a, 134b will be larger than that of the second chambers 234a, 234b, and the working volume of the first and second piston elements 122a, 122b the first rotor will be greater than the working volume of the first and second piston elements 222a, 222b of the second rotor.

Since the shaft 118 of the first flow path 111 (first rotor 119) and the shaft 218 of the first flow path 115 (second rotor 219) are connected for joint rotation, the first rotor 119 drives both the motor 308 and the expansion of the fluid in the subchambers 234a1, 234a2, 234b1, 234b2 of the second rotor 219.

In other examples, the first rotor shaft 118 and the second rotor shaft 218 are one-piece and extend through both rotors 119, 219. The operation of the device 200 will be disclosed below. Stage 1

In the example of FIG. 16, the working fluid enters the subchambers 134a1, 134b1 through the first port 114a and the fifth port 114c, respectively.

Next, the working fluid is pumped (e.g., compressed) under the action of the respective first and second piston elements 122a, 122b, driven by the motor 308, in the subchambers 134a, 134b and exits through the second port 114b and the sixth port 114d, respectively.

Simultaneously with the withdrawal of the working fluid into the subchambers 134a1, 134b1, the working fluid is discharged from the subchambers 134a2, 134b2 through the second port 114b and the sixth port 114d, respectively.

Simultaneously with the discharge of the working fluid from the subchambers 134a1, 134b1, the working fluid is taken into the subchambers 134a2, 134b2 through the first port 114a and the fifth port 114c, respectively.

Stage 2

In the example of FIG. 16, after discharging from the chamber 134a, 134b of the first rotor, the working fluid flows through the channels 300a1, 300b1, respectively, and enters the first heat exchanger 302a, which acts as a heat sink. Therefore, heat is removed from the working fluid as it passes through the first heat exchanger 302a.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the first heat exchanger 302a.

Stage 3

In the example of FIG. 16, the working fluid passes through the channels 300a2, 300b2 and enters the subchambers 234b1, 234a1 of the second rotor through the third window 116a and the seventh window 116c, respectively, where its pressure is limited, and the working fluid is dosed into the channels 304a1, 304b1, respectively, through the fourth window 116b and eighth window 116d, respectively.

Simultaneously with the entry of the working fluid into the subchambers 234b1, 234a1, the working fluid is discharged from the subchambers 234b2, 234a2 through the fourth port 116b and the eighth port 116d, respectively.

As the second rotor 219 continues to rotate, the working fluid is released from the subchambers 234b1, 234a1 through the fourth port 116b and the eighth port 116d, and more of the working fluid enters the subchambers 234b2, 234a2 through the third port 116a and the seventh port 116c.

In all examples, the sequential supply and behavior of the working fluid in the rotor subchambers 234a1, 234a2, 234b1, 234b2 creates a force under which (at least partially) the second rotor 219 rotates around its second axis of rotation 232 and the rotor rotates around its first axis of rotation. This force is in addition to the force generated by the 308 motor.

Stage 4

In the example of FIG. 16, the working fluid then flows from the chambers 234a, 234b of the second rotor through the channels 304a2, 304b2 and enters the second heat exchanger 306a, in this example made as a heat source.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the second heat exchanger 306a.

Thus, the working fluid absorbs heat from the heat source, and then leaves the second heat exchanger 306a and passes through the channels 304a2, 304b2, before entering the chambers 134a, 134b of the first rotor to start a new cycle.

EXAMPLE 3 - SINGLE UNIT, CLOSED CIRCUIT, THERMAL ENGINE

FIG. 19 illustrates an example of a closed loop heat engine (eg, a power harvesting generator) apparatus 400 of the present disclosure having a variety of features in common with the example of FIG. 15 or potentially physically identical or equivalent to its features, in connection with which the same reference numbers have been used.

The example in FIG. 19 is different from the example in FIG. 15 in that, instead of the motor 308, the PTO 408 is operatively connected to the first shaft 118. Power take-off 408 may be configured as a gear clutch to drive another device, such as an electric generator.

In addition, the first heat exchanger 302a is configured as a heat source (rather than a heat sink in Example 1) and the second heat exchanger 306a is configured as a heat sink (rather than a heat source in Example 1). Otherwise, the Examples in FIG. 15, 19 are structurally the same.

In other words, in practice, if the heat sink and heat source of the equipment configured as the heat pump in FIG. 15 would be exchanged for one another, and the motor 308 in FIG. 15 would be changed to generator 408, resulting in the heat engine of FIG. nineteen.

In other words, in practice, in the presence of a thermodynamically reversible heat source and heat sink, as well as a motor 308, also configured to work as a generator 408, then the circuit could be thermodynamically reversible with the possibility of functioning as a heat pump 100, or in the opposite direction as a heat engine 400 in applications where this would be considered an advantage.

As a consequence, during operation, the direction of fluid flow through the system in FIG. 19 and, therefore, the thermodynamic process is the opposite of what occurs in the system of FIG. fifteen.

Thus, the subchambers 134a1, 134a2 (i.e., the first flow portion 111) are configured to function as displacement / compression chambers in the example of FIG. 15 are configured to function as expansion chambers in the example of FIG. 19. In other words, in this example, the first chamber 134a and the first piston element 122a (ie, the first flow portion 111) are configured to function as part of the fluid expansion.

In addition, the subchambers 134b1, 134b2 (i.e., the second flow portion 115) configured to function as metering / expansion chambers in the example of FIG. 15 are configured to function as displacement / compressor / pump chambers in the example of FIG. 19. In other words, in this example, the second chamber 134b and the second piston element 122b (ie, the second flow path 115) may be configured to function as a fluid displacement pump or compressor.

Therefore, since the expansion portion (i.e., the first flow portion 111) and the displacement portion (i.e., the second flow portion 115) are two sides of the same rotor, the rotor 119 causes the expansion of the working fluid in the first chamber 134a to rotate. (i.e. in sub-cameras 134a1, 134a2).

The operation of the device 400 will be disclosed below.

Stage 1

In the example of FIG. 19, the working fluid flows through the channel 300a1 and through the second window 114b enters the rotor subchamber 134a2, where it expands.

Simultaneously with the entry of the working fluid into the subchamber 134a2 and its expansion in it, the working fluid is discharged from the subchamber 134a1 through the first port 114a.

As the rotor 119 continues to rotate, the working fluid is released from the subchamber 134a2 through the first port 114a, and through the second port 114b, more working fluid enters the subchamber 134a1, where it expands.

In all examples, the sequential expansion of the working fluid in the rotor subchambers 134a1, 134a2 creates a force that pivots the rotor about its second axis of rotation 132 and rotates the rotor about its first axis 130 of rotation. The force due to rotation drives the generator 408 through the shaft 118.

Stage 2

In the example of FIG. 19, after being discharged from the first chamber 134a of the rotor 119, the working fluid passes through the passage 304a2 and enters the second heat exchanger 306a, which is configured as a heat sink. Therefore, heat is removed from the working fluid as it passes through the second heat exchanger 306a.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the second heat exchanger 306a.

Stage 3

In the example of FIG. 19, working fluid enters the sub-chamber 134b2 through the fourth port 116b.

Next, the working fluid is displaced / pumped under the action of the second piston element 122b, driven by the expansion of the working fluid in the first chamber 134a, and exits through the third port 116a.

Simultaneously with the withdrawal of the working fluid into the subchamber 134b2, the working fluid is discharged from the subchamber 134b1 through the third port 116a.

Simultaneously with the discharge of the working fluid from the subchamber 134b2, the working fluid is taken into the subchamber 134b1 through the fourth port 116b.

Stage 4

In the example of FIG. 19, the working fluid then flows from the second chamber 134b through the channel 300a2 and enters the first heat exchanger 302a, which is configured as a heat source.

Thus, the working fluid absorbs heat from the heat source and then leaves the first heat exchanger 302a and passes through the channel 300a1, before entering the first chamber 134a to start a new cycle.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the first heat exchanger 302a.

EXAMPLE 4 - DUAL UNIT, CLOSED CIRCUIT, THERMAL MOTOR

FIG. 20 illustrates a second example of a closed-loop heat engine (eg, a power plant), apparatus 500 according to the present disclosure, which includes a variety of features in common with the example of FIG. 16 or equivalent to its features, in connection with which the same item numbers are used.

The example in FIG. 20 is different from the example in FIG. 16 in that, instead of the motor 308, the power take-off 408 is connected to the first shaft 118 so that it can be driven therewith. Power take-off 408 may be configured as a gear clutch to drive another device, such as an electric generator.

In addition, the first heat exchanger 302a is configured as a heat source (rather than a heat sink in Example 2), and the second heat exchanger 306a is configured as a heat sink (and not a heat source in Example 2). Otherwise, the examples in FIG. 16, 20 are structurally the same.

In other words, in practice, if the heat sink and heat source of the equipment configured as the heat pump in FIG. 16 would be swapped for one another, and the motor 308 of the example in FIG. 16 would be changed to generator 408, resulting in the heat engine of FIG. twenty.

As a consequence, during operation, the direction of fluid flow through the system in FIG. 20 and, therefore, the thermodynamic process is the opposite of what occurs in the system of FIG. sixteen.

Therefore, the first rotor subchambers 134a1, 134a2, 134b1, 134b2 (i.e., the first flow portion 111) configured to function as displacement / compression chambers in the example of FIG. 16 are configured to function as expansion chambers in the example of FIG. 20. In other words, in this example, the first chamber 134a of the first rotor and the first piston element 122a, and the second chamber 134b of the first rotor and the second piston element 122b (i.e., the first flow path 111) are configured to function as part of the fluid expansion. ...

In addition, subchambers 234a1, 234a2, 234b1, 234b2 (i.e., second flow portion 115) configured to function as expansion / metering chambers in the example of FIG. 16 are configured to function as displacement / compressor / pump chambers in the example of FIG. 20. In other words, in this example, the first chamber 234a of the second rotor and the first piston element 222a, and the second chamber 234b of the second rotor and the second piston element 222b (i.e., the second flow path 115) may be configured to function as a displacement pump fluid or compressor.

Since the shaft 118 of the first flow path 111 (first rotor 119) and the shaft 218 of the second flow path 115 (second rotor 219) are connected, they rotate together.

Therefore, since the shaft 118 of the expansion portion (i.e., the first flow portion 111) and the shaft 218 of the displacement portion (i.e., the second flow portion 115) are rotatably coupled, the second rotor 219 causes the expansion of the working fluid in the chamber 134a to rotate. , b of the first rotor (i.e., in subchambers 134a1, 134a2, 134b1, 134b2).

Similar to Example 2 in FIG. 16, the first chamber 134a and the second chamber 134b of the first rotor 119 (i.e., the first flow portion 111) have substantially equal volumetric capacity. The first chamber 234a and the second chamber 234b of the second rotor 219 (i.e., the second flow path 115) have substantially equal volumetric capacity. In this case, the volumetric capacity of the chambers 134a, 134b of the first rotor (first flow part 111) can be substantially equal to the volumetric capacity of chambers 234a, 234b of the second rotor (second flow part 115), be less or more than it.

In other words, in this example, the volumetric capacity of the chambers 234a, 234b of the rotor of the second flow passage 115 can be equal to the volumetric capacity of the chambers 134a, 134b of the rotor of the first flow passage 111, be less or greater than it.

In other words, in this example, the volumetric capacity of the second flow portion 115 can be no more than half the volumetric capacity of the first flow portion 111.

Alternatively, in this example, the volumetric capacity of the second flow portion 115 may be at least twice the volumetric capacity of the first flow portion 111.

As disclosed in FIG. 18, showing only rotors 119, 219, the first and second piston elements 122, 222 and shafts 118, 218, the difference in volumetric capacity can be achieved by making the chambers 134a, 134b of the first rotor wider than chambers 234a, 234b of the second rotor, when the first and second piston members 122a, 122b of the first rotor will therefore be wider than the first and second piston members 222a, 222b of the second rotor. Therefore, although the first and second piston elements 122, 222 can rotate through the same angle, the volume of the first chambers 134a, 134b will be larger than that of the second chambers 234a, 234b, and the working volume of the first and second piston elements 122a, 122b the first rotor will be greater than the working volume of the first and second piston elements 222a, 222b of the second rotor.

The operation of the device 500 will be disclosed below.

Stage 1

In the example of FIG. 20, the working fluid flows through the channels 300a1, 300b1 and flows through the second port 114b and the sixth port 114d, respectively, into the subchambers 134a2, 134b2, respectively, of the first rotor 119, where it expands.

Simultaneously with the entry of the working fluid into the subchambers 134a2, 134b2 and its expansion in them, the working fluid is discharged from the subchamber of the first rotor 134a1, 134a2 through the first port 114a and the fifth port 114c, respectively.

As the rotation of the first rotor 119 continues, the working fluid is released from the subchambers 134a2, 134b2 through the first port 114a and the fifth port 114c, respectively, and a larger amount of the working fluid enters through the second port 114b and the sixth port 114d into the subchambers 134a1, 134a2, where it is expanding.

In all examples, the sequential expansion of the working fluid in the rotor subchambers 134a1, 134a2, 134b1, 134b2 creates a force that pivots the first rotor about its second axis of rotation 132 and rotates the first rotor 119 about its first axis 130 of rotation. The force due to rotation drives the generator 408 through the shaft 118.

Stage 2

In the example of FIG. 20, after being discharged from the first chambers 134a, 134b of the first rotor 119, the working fluid flows through the channels 304a2, 304b2, respectively, and enters the second heat exchanger 306a, which is configured as a heat sink. Therefore, heat is removed from the working fluid as it passes through the second heat exchanger 306a.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the second heat exchanger 306a.

Stage 3

In the example of FIG. 20, the working fluid enters the subchambers 234b2, 234a2 of the second rotor through the fourth port 116b and the eighth port 116d, respectively.

Next, the working fluid is displaced / pumped under the action of the first and second piston elements 222a, 222b of the second rotor, driven by the expansion of the working fluid in the chambers 134a, 134b of the first rotor, and its exit through the third window 116a and the seventh window 116, respectively.

Simultaneously with the withdrawal of the working fluid into the subchambers 234b2, 234a2 of the second rotor, the working fluid is discharged from the subchambers 234b1, 234a1 of the second rotor through the third window 116a and the seventh window 116c, respectively.

Simultaneously with the discharge of the working fluid from the subchambers 234b2, 234a2 of the second rotor, the working fluid is taken into the subchambers 234b1, 234a1 of the second rotor through the fourth port 116b and the eighth port 116d, respectively.

Stage 4

In the example of FIG. 20, the working fluid then flows from the second chambers 234b, 234a of the second rotor through the channels 300a2, 300b2 and enters the first heat exchanger 302a, which serves as a heat source.

Thus, the working fluid absorbs heat from the heat source and then leaves the first heat exchanger 302a and passes through the channels 300a1, 300b1, before entering the first chambers 134a, 134b of the first rotor to start a new cycle.

Depending on the nature of the working fluid, a phase transition of the working fluid is possible in the first heat exchanger 302a.

EXAMPLE 5 - SINGLE UNIT, OPEN CIRCUIT, THERMAL ENGINE

FIG. 21 illustrates a first example of an open loop power plant (heat engine) device 600 according to the present disclosure, which includes a variety of features in common with the example of FIG. 19 or equivalent, for which the same reference numbers are used.

The example in FIG. 21 is different from the example in FIG. 19 next.

The system is an open loop, with no communication between the first window 114a and the fourth window 116b. In other words, the second passage 304a and the second heat exchanger 306a are absent, whereby the first port 114a and the fourth port 116b are isolated from each other.

The fourth window 116b may be in fluid communication with an air source, for example, in communication with the atmosphere. Therefore, in this example, the working fluid may include air.

The first heat exchanger 302a may include or be thermally associated with any suitable heat source (eg, solar heat, waste or flue gases from another process, or steam). Alternatively, the first heat exchanger 302a may include a combustion chamber 602 configured to burn continuously. For example, the combustion chamber may include a burner that is fueled with fuel to generate heat. The combustion process can be a continuous combustion process.

Therefore, as in Example 3 in FIG. 19, the first heat exchanger 302a is a heat source configured to transfer thermal energy to a fluid passing therethrough.

The volumetric capacity of the second chamber 134b of the first rotor may be substantially equal to, less than or greater than, the volumetric capacity of the first chamber 134a of the first rotor.

In other words, in this example, the volumetric capacity of the second flow portion 115 may be equal to the volumetric capacity of the first flow portion 111, be less or greater than it.

For example, the volumetric capacity of the second chamber 134b of the first rotor may be no more than half the volumetric capacity of the first chamber 134a of the first rotor.

Alternatively, the volumetric capacity of the second chamber 134b of the first rotor may be at least twice the volumetric capacity of the first chamber 134a of the first rotor.

In this example, this provides some degree of expansion within a single device (eg, disclosed in FIG. 17).

This can be achieved by making the first chamber 134a of the first rotor different in width from the second chamber 134b of the first rotor, whereby, as a consequence, the width of the first piston element 122a is different from the width of the second piston element 122b. Therefore, although the piston members rotate and thus move by the same amount about the second axis of rotation 132, the volume of the chambers 134a, 134b and the working volume of the first and second piston members 122a, 122b will be different from each other.

As disclosed in FIG. 17 showing only the rotor assembly 116, different volumes can be achieved by making the first chamber 134a of the first rotor wider than the second chamber 134b of the first rotor, whereby as a consequence the first piston element 122a is wider than the second piston element 122b. Therefore, although the piston elements rotate and thus move by the same amount about the second axis of rotation 132, the volume of the chambers 134a will be greater than the volume of the chamber 134b and thus the working volume of the first piston element 122a will be greater than at the second piston element 122b.

The operation of the device 600 will be disclosed below.

Stage 1

In the example of FIG. 21, working fluid (eg, air) enters the sub-chamber 134b2 through the fourth port 116b.

Next, the working fluid is displaced / compressed / dispensed under the action of the second piston element 122b, driven by the expansion of the working fluid in the first chamber 134a (as disclosed below in Step 3) and exits through the third port 116a.

Simultaneously with the withdrawal of the working fluid into the subchamber 134b2, the working fluid is discharged from the subchamber 134b1 through the third port 116a.

Simultaneously with the discharge of the working fluid from the subchamber 134b2, the working fluid is withdrawn into the subchamber 134b1 through the fourth port 116b.

Stage 2

In the example of FIG. 21, the working fluid then flows from the second chamber 134b through the channel 300a2 and enters the first heat exchanger 302a, which is configured as a heat source.

The working fluid can be mixed with fuel in the combustion chamber 603 for partial combustion and partial heating with increasing pressure, after which it enters the second port 114b of the expansion part, in this example the first flow part 111.

Thus, the working fluid absorbs heat from the heat source and then leaves the first heat exchanger 302a and passes through the channel 300a1 before entering the first chamber 134a.

Stage 3

In the example of FIG. 21, the working fluid flows through the channel 300a1 and through the second window 114b enters the rotor subchamber 134a2, where it expands.

Simultaneously with the entry of the working fluid into the subchamber 134a2 and its expansion in it, the working fluid is discharged from the subchamber 134a1 through the first port 114a.

As the rotor 119 continues to rotate, the working fluid is discharged from the subchamber 134a2 through the first port 114a, and more of the working fluid enters the subchamber 134a1 through the second port 114b, where it expands.

Thus, there is a sequential expansion of the exhaust gas in the subchambers 134a1, 134a2 of the first chamber 134a (due to which the gas pressure drops and its volume increases), as a result of which the gas acts on the first piston element 122a to force the first piston element 122a to move through the chamber 134a (functioning as an expansion chamber), thereby moving the second piston element 122b through the second chamber 134b to draw and compress further air to restart the process.

Thus, the successive expansion of the working fluid in the subchambers of the rotor 134a1, 134a2 creates a force under which the rotor rotates about its second axis of rotation 132 and the rotor rotates about its first axis of rotation 130. The force due to rotation drives the generator 408 through the shaft 118.

EXAMPLE 6 - DUAL UNIT, OPEN CIRCUIT, THERMAL MOTOR

FIG. 22 illustrates a second example of an open loop power plant (heat engine) device 700 according to the present disclosure, which includes a variety of features common or equivalent to those of the example in FIG. 20, whereby the same reference numbers are used.

The example in FIG. 22 is different from the example in FIG. 20 next.

The system is an open loop, with no connection between the second rotor flow inlets (in this example, the fourth port 116b and the eighth port 116d) and the first rotor flow outlets (in this example, the first port 114c and the fifth port 114c), respectively. In other words, the second passage 304a and the second heat exchanger 306a of Example 4 (FIG. 20) are not present in the example in FIG. 22, whereby the fourth window 116b and the first window 114a are isolated from each other, and the eighth window 116d and the fifth window 114c are isolated from each other.

The fourth port 116b and the eighth port 116d may be in fluid communication with an air source, such as the atmosphere. Therefore, in this example, the working fluid may include air.

As in the example in FIG. 20, the first heat exchanger 302a may include or be thermally associated with any suitable heat source (eg, solar heat, waste or flue gases from another process, or steam). Alternatively, as in Example 5 in FIG. 21, the first heat exchanger 302a may include a combustion chamber 602 configured to burn continuously. For example, the combustion chamber may include a burner that is fueled with fuel to generate heat. The combustion process can be a continuous combustion process. Therefore, as in the example in FIG. 20, the first heat exchanger 302a is configured to transfer thermal energy to a fluid passing therethrough.

A combustion chamber 602a, 602b may be configured for each fluid circuit. Chambers 602a, 602b may be fluidly isolated from each other. Therefore, the first combustor 602a can be fluidly coupled to the bore 300a and the second combustor 602b can be fluidly coupled to the bore 300b. Combustion chambers 602a, 602b may be located within a single combustion chamber block 602.

The operation of the device 700 will be disclosed below.

Stage 1

In the example of FIG. 22, the working fluid (eg, air) enters the subchambers 234b2, 234a2 of the second rotor through the fourth port 116b and the eighth port 116d, respectively.

Next, the working fluid is displaced / compressed / dispensed under the action of the first and second piston elements 222a, 222b of the second rotor, driven by the expansion of the working fluid in the first chambers 134a, 134b of the first rotor (as disclosed below in Step 3), and its output through the third window 116a and the seventh window 116c, respectively.

Simultaneously with the withdrawal of the working fluid into the subchambers 234b2, 234a2, the working fluid is discharged from the subchambers 234b1, 234a1 through the third port 116a and the seventh port 116c, respectively.

Simultaneously with the discharge of the working fluid from the subchambers 234b2, 234b1, the working fluid is taken into the subchambers 234b1, 234a1 through the fourth port 116b and the eighth port 116d, respectively.

Stage 2

In the example of FIG. 22, the working fluid then flows from the second chambers 234b, 234a through the channels 300a2, 300b2 of the second rotor and enters the first heat exchanger 302a, which is configured as a heat source.

The working fluid can be mixed with fuel in the combustion chamber 603 for its partial combustion and partial heating with increasing pressure, after which it enters the second port 114b and the sixth port 114d of the first rotor 119 (i.e., the first flow passage 111 or "expansion " part).

Thus, the working fluid absorbs heat from the heat source and then leaves the first heat exchanger 302a and passes through the channels 300a1, 300b1, before entering the chambers 134a, 134b of the first rotor.

Stage 3

In the example of FIG. 22, the working fluid flows through the channels 300a1, 300b1 and flows through the second port 114b and the sixth port 114d into the subchambers 134a2, 134a2 of the first rotor 119, where it expands.

Simultaneously with the entry of the working fluid into the subchambers 134a2, 134b2 and its expansion in them, the working fluid is released from the subchambers 134a1, 134b1 through the first window 114a and the fifth window 114c, respectively.

As the rotation of the first rotor 119 continues, the working fluid is released from the subchambers 134a2, 134b2 through the first port 114a and the fifth port 114c, while a larger amount of the working fluid through the second port 114b and the sixth port 114d enters the subchambers 134a1, 134b1, where it is expanding.

Thus, there is a sequential expansion of the exhaust gas in the subchambers 134a1, 134a2, 134b1, 134b2 of the chambers 134a, 134b of the first rotor (due to which the gas pressure drops and its volume increases), as a result of which the gas acts on the first and second piston elements 122a, 122b of the first rotor to force the first piston element 122a through chamber 134a (functioning as an expansion chamber) and to force the second piston element 122b through chamber 134b (functioning as an expansion chamber), i.e. to drive the first and second piston elements 122a, 122b through the respective chambers 134a, 134b for sampling the next portion of air in order to restart the process.

Thus, the sequential expansion of the working fluid in the subchambers 134a1, 134a2, 134b1, 134b2 of the first rotor creates a force that pivots the first rotor 119 about its second axis of rotation 132 and rotates the first rotor about its first axis 130 of rotation. The force due to rotation drives the generator 408 through the shaft 118.

Since the shaft 118 of the expansion portion (i.e., the first flow portion 111) and the shaft 218 of the displacement portion (i.e., the second flow portion 115) are rotatably coupled, the second rotor 219 causes the expansion of the working fluid in the chambers 134a to rotate, b of the first rotor (i.e. in subchambers 134a1, 134a2, 134b1, 134b2).

EXAMPLE 7 - SINGLE UNIT, OPEN CIRCUIT, THERMAL ENGINE

FIG. 23 illustrates a third example of an open loop heat engine (power plant) apparatus 800 according to the present disclosure, which includes a variety of features common or equivalent to those of the example of FIG. 21, whereby the same reference numbers are used.

The example in FIG. 23 is different from the example in FIG. 21 next.

The fourth window 116b is configured for fluid communication with a source of hot gas, such as flue or exhaust gases. Therefore, in this example, the working fluid may include a source of hot gas, such as flue or exhaust gases.

The first heat exchanger 302a includes a chamber 810 configured to pass a fluid flow between the displacement portion (in this example, the second flow portion 115) and the expansion portion (in this example, the first flow portion 111), and a nozzle 812 configured to inject cryogenic medium into the chamber 810, resulting in the transfer of thermal energy from the fluid to the cryogenic media to increase their pressure. Thus, the first heat exchanger 302a is configured to extract heat energy from the working fluid passing through it, at which the pressure of the cryogenic medium increases, that is, it is designed as a heat sink.

The cryogenic fluid can be a gas under normal atmospheric conditions, stored in a compressed or liquefied state, or in a state in which heat must be supplied to return to the gas phase, such as liquid nitrogen or liquefied air. In the present disclosure, the expression "cryogenic fluid" means any medium stored in a low temperature liquid state or gaseous state, when heat is applied to which it will expand, possibly aggressive.

The volumetric capacity of the second chamber 134b of the first rotor may be substantially equal to, less than or greater than, the volumetric capacity of the first chamber 134a of the first rotor.

In other words, in this example, the volumetric capacity of the second flow portion 115 may be equal to the volumetric capacity of the first flow portion 111, be less or greater than it.

For example, the volumetric capacity of the second chamber 134b of the first rotor may be no more than half the volumetric capacity of the first chamber 134a of the first rotor.

Alternatively, the volumetric capacity of the second chamber 134b of the first rotor may be at least twice the volumetric capacity of the first chamber 134a of the first rotor.

In this example, this provides some degree of expansion within a single device (eg, disclosed in FIG. 17).

This can be achieved by making the first chamber 134a of the first rotor different in width from the second chamber 134b of the first rotor, whereby, as a consequence, the width of the first piston element 122a is different from the width of the second piston element 122b. Therefore, although the piston members rotate and thus move by the same amount about the second axis of rotation 132, the volume of the chambers 134a, 134b and the working volume of the first and second piston members 122a, 122b will be different from each other.

As disclosed in FIG. 17, showing only the rotor assembly 116, different volumes can be achieved by making the first chamber 134a of the first rotor wider than the second chamber 134b of the first rotor, whereby the width of the first piston element 122a is greater than the width of the second piston element 122b. Therefore, although the piston elements will rotate and thus move by the same amount about the second axis of rotation 132, the volume of the chambers 134a will be greater than the volume of the chamber 134b and, thus, the working volume of the first piston element 122a will be greater than at the second piston element 122b.

The operation of the device 800 will be discussed below.

Stage 1

In the example of FIG. 23, the working fluid enters the sub-chamber 134b2 through the fourth port 116b.

Next, the working fluid is displaced / metered by the second piston element 122b, driven by the expansion of the working fluid in the first chamber 134a (as disclosed below), and exits through the third port 116a.

Simultaneously with the withdrawal of the working fluid into the subchamber 134b2, the working fluid is discharged from the subchamber 134b1 through the third port 116a.

Simultaneously with the discharge of the working fluid from the subchamber 134b2, the working fluid is taken into the subchamber 134b1 through the fourth port 116b.

Stage 2

In the example of FIG. 23, the working fluid then flows from the second chamber 134b through the channel 300a2 and enters the first heat exchanger 302a, which is configured as a heat sink.

In the chamber 810, the hot gas can be mixed with the cryogenic medium with the transfer of heat to the cryogenic medium, as a result of which its pressure increases, after which it enters the second window 114b of the expansion part (in this example, the first flow part 111).

Thus, the cryogenic medium is mixed with the working fluid and the first heat is absorbed from the latter, after which the cryogenic medium leaves the first heat exchanger 302a and passes through the channel 300a1 before entering the first chamber 134a.

Stage 3

In the example of FIG. 23, the working fluid passes through the channel 300a1 and enters the rotor subchamber 134a2 through the second port 114b, where it expands.

Simultaneously with the entry of the working fluid into the subchamber 134a2 and its expansion in it, the working fluid is discharged from the subchamber 134a1 through the first port 114a.

As the rotor 119 continues to rotate, the working fluid is discharged from the subchamber 134a2 through the first port 114a, while through the second port 114b, more working fluid enters the subchamber 134a1, where it expands.

Thus, there is a sequential expansion of the mixture of exhaust gas and cryogenic medium in the subchambers 134a1, 134a2 of the first chamber 134a (due to which the gas pressure drops and its volume increases), as a result of which the gas acts on the first piston element 122a to force the first piston element 122a through chamber 134a (functioning as an expansion chamber), thereby moving the second piston member 122b through the second chamber 134a to collect and compress / expel another portion of working fluid to restart the process.

Thus, the sequential expansion of the working fluid in the subchambers of the rotor 134a1, 134a2 creates a force under which the rotor rotates about its second axis of rotation 132 and the rotor rotates about its first axis 130 of rotation. The force due to rotation drives the generator 408 through the shaft 118.

EXAMPLE 8 - DUAL UNIT, OPEN CIRCUIT, THERMAL MOTOR

FIG. 24 illustrates a fourth example of an open loop heat engine power plant, i. E. device 900 according to the present disclosure, which includes a variety of features common or equivalent to those of the example in FIG. 22, whereby the same reference numbers are used.

The example in FIG. 24 is different from the example in FIG. 22 in that the flow inlets of the second rotor (in this example they are the fourth port 116b and the eighth port 116d) are arranged in fluid communication with a source of hot gas, such as flue or exhaust gases.

Therefore, in this example, the working fluid may include a source of hot gas, such as flue or exhaust gases.

As in Examples 2, 4, 6, the first chamber 134a and the second chamber 134b of the first rotor 119 (i.e., the first flow portion 111) have substantially the same volumetric capacity (i.e., the same volume). The first chamber 234a and the second chamber 234b of the second rotor 219 (i.e., the second flow path 115) have substantially equal volumetric capacity (i.e., the same volume). In this case, the volumetric capacity (i.e. volume) of the chambers 134a, 134b of the first rotor (first flow part 111) can be substantially equal to the volumetric capacity (i.e. volume) of the chambers 234a, 234b of the second rotor (second flow part 115), be less or more than her.

In other words, in this example, the volumetric capacity (i.e., the volume) of the chambers 234a, 234b of the rotor of the second flow path 115 may be equal to the volumetric capacity (i.e., the volume) of the chambers 134a, 134b of the rotor of the first flow path 111, be less or more her.

In other words, in this example, the volumetric capacity of the second flow portion 115 can be no more than half the volumetric capacity of the first flow portion 111.

Alternatively, in this example, the volumetric capacity of the second flow portion 115 may be at least twice the volumetric capacity of the first flow portion 111.

In addition, as in the example in FIG. 23, the first heat exchanger 302a comprises a chamber 810 configured to pass a fluid flow between the displacement part (in this example, the second rotor 219, i.e., the second flow part 115) and the expansion part (in this example, the first rotor 119, i.e. e. the first flow portion 111), and a nozzle 812 configured to inject a cryogenic medium into the chamber 810, thereby transferring thermal energy from the fluid to the cryogenic medium to increase its pressure. Thus, the first heat exchanger 302a is configured to extract heat energy from the working fluid passing through it, at which the pressure of the cryogenic medium increases, that is, it is designed as a heat sink.

A mixing chamber 810a, 810b and a nozzle 812 may be provided for each fluid circuit. The chambers 810a, 810b may be fluidly isolated from each other. That is, a first cryogenic chamber 810a in fluid communication with conduit 300a and a second cryogenic chamber 810b in fluid communication with conduit 300b may be provided. Mixing chambers 810a, 801b may be located within a single mixing chamber block 810.

The operation of the device 900 will be disclosed below.

Stage 1

In the example of FIG. 23, the working fluid enters the subchambers 234b2, 234a2 of the second rotor through the fourth port 116b and the eighth port 116d, respectively.

Next, the working fluid is displaced / compressed / dispensed under the action of the first and second piston elements 222a, 222b of the second rotor, driven by the expansion of the working fluid in the first chambers 134a, 134b of the first rotor (as disclosed below in Step 3), and its output through the third window 116a and the seventh window 116c, respectively.

Simultaneously with the withdrawal of the working fluid into the subchambers 234b2, 234a2, the working fluid is discharged from the subchambers 234b1, 234a1 through the third port 116a and the seventh port 116c, respectively.

Simultaneously with the release of the working fluid from the subchambers 234b2, 234b1, the working fluid is taken into the subchambers 234b1, 234a1 through the fourth port 116b and the eighth port 116d, respectively.

Stage 2

In the example of FIG. 24, the working fluid then flows from the second chambers 234b, 234a of the second rotor through the channels 300a2, 300b2 and enters the first heat exchanger 302a, which acts as a heat sink.

Mixing chamber 810 can mix the hot gas with the cryogenic medium with the transfer of heat to the cryogenic medium, as a result of which its pressure increases, after which it enters the second port 114b and the sixth port 114d of the first rotor 119 (i.e., the first flow path 111 or "Expansion part").

Thus, the cryogenic medium is mixed with the working fluid and the first heat is absorbed from the latter, after which the cryogenic medium leaves the first heat exchanger 302a and passes through the channels 300a1, 300b1, before entering the chambers 134a, 134b of the first rotor.

Stage 3

In the example of FIG. 24, the working fluid flows through the channels 300a1, 300b1 and through the second port 114b and the sixth port 114d enters the subchambers 134a2, 134a2 of the first rotor 119, where it expands.

Simultaneously with the entry of the working fluid into the subchambers 134a2, 134b2 and its expansion in them, the working fluid is discharged from the subchambers 134a1, 134b1 through the first port 114a and the fifth port 114c, respectively.

As the rotation of the first rotor 119 continues, the working fluid is discharged from the subchambers 134a2, 134b2 through the first window 114a and the fifth window 114c, while through the second window 114b and the sixth window 114d a larger amount of the working fluid enters the subchambers 134a1, 134b1, where it is expanding.

Thus, there is a sequential expansion of the exhaust gas in the subchambers 134a1, 134a2, 134b1, 134b2 of the chambers 134a, 134b of the first rotor (due to which the gas pressure drops and its volume increases), as a result of which the gas acts on the first and second piston elements 122a, 122b of the first rotor to force the first piston element 122a through chamber 134a (functioning as an expansion chamber) and to force the second piston element 122b through chamber 134b (functioning as an expansion chamber), i.e. to drive the first and second piston elements 122a, 122b through the respective chambers 134a, 134b for sampling the next portion of air in order to restart the process.

Thus, the sequential expansion of the working fluid in the subchambers 134a1, 134a2, 134b1, 134b2 of the first rotor creates a force that pivots the first rotor 119 about its second axis of rotation 132 and rotates the first rotor about its first axis 130 of rotation. The force due to rotation drives the generator 408 through the shaft 118.

Since the shaft 118 of the expansion portion (i.e., the first flow portion 111) and the shaft 218 of the displacement portion (i.e., the second flow portion 115) are rotatably coupled, the second rotor 219 causes the expansion of the working fluid in the chamber 134a to rotate, b of the first rotor (i.e. in subchambers 134a1, 134a2, 134b1, 134b2).

EXAMPLES OF DUAL UNIT OPTIONS

In alternative examples of twin installations (for example, the variants of Example 2 (Fig. 16), Example 4 (Fig. 20), Example 6 (Fig. 22) and Example 8 (Fig. 24), the first chamber 134a of the first rotor may have a volumetric capacity substantially less than or substantially greater than the volumetric capacity of the second chamber 134b of the first rotor Also or alternatively, the second chamber 234b of the second rotor may have a volumetric capacity substantially less or substantially greater than the volumetric capacity of the first chamber 234a of the second rotor.

For example, the volumetric capacity of the first chamber 134a of the first rotor may be no more than half or at least twice the volumetric capacity of the second chamber 134b of the first rotor. Additionally or alternatively, the volumetric capacity of the second chamber 234b of the second rotor may be at most half or at least twice the volumetric capacity of the first chamber 234a of the second rotor.

In such an example, a multistage device or two loops of working fluid with different degrees of expansion are created within the same system.

Channels 300a, 300b and channels 304a, 304b are illustrated as separate loops. In this way, channel 300a and channel 300b can be at least partially combined to form a common flow path through heat exchanger 302. Likewise, channel 304a and channel 304b can at least partially be combined to form a common flow path flow passing through heat exchanger 306. Alternatively, channels 300a, 300b can pass through completely separate heat exchange units 302 with different or identical heat capacities. Likewise, alternatively, channels 304a, 304b may pass through completely separate heat exchange units 306 with different or identical heat capacities.

The previous examples disclose that the drive shafts 118, 218 are rigidly / directly coupled so that they operate at the same rotational speed with no loss between them. In this case, in an alternative example, the first shaft 118 and the second shaft 218 can be connected by mechanical means (for example, a gearbox) or virtual means (for example, by means of an electronic control system) with the possibility of rotation at different frequencies relative to each other.

The core of the device of the present disclosure is a true volumetric displacement unit capable of reducing internal volume by up to 100%, inclusive, per revolution. It is configured to simultaneously "compress" and "expand" the piston element 122 in a corresponding chamber; for example, in the same chamber, it can create a full vacuum on one side of the piston element while being compressed and / or displaced on the other side.

The connection of the displacement portion and the expansion portion (i.e., direct transmission between the first flow portion 111 and the second flow portion 115, regardless of whether they are part of the same rotor, as disclosed in FIGS. 15, 19, 21, 23 or coupled rotors as disclosed in Figures 16, 20, 22, 24) minimizes mechanical losses compared to prior art examples, and also allows energy to be recovered from processes in each of the portions to facilitate activation of the other side.

This makes it possible to significantly increase the attainable ratios of expansion or contraction compared to prior art examples. For example, in a single stage, an expansion or contraction ratio of more than 10: 1 can be achieved, which is significantly higher than in the prior art examples.

Volumetric displacement due to continuous (and simultaneous) expansion and displacement / contraction processes on opposite sides of the same piston element makes it possible to create a device that is inherently more efficient than known devices.

This also means that the device is able to operate efficiently at varying loads and speeds, which is not possible with traditional configurations (for example, those that include an axial turbine). This provides the ability to harvest energy at previously unattainable input levels.

The proposed device can be scaled to any size depending on the desired performance and energy requirements, while its dual secondary drive shaft also facilitates the installation of multiple drive devices on a common shaft, which increases productivity, uniformity, power output, provides redundancy or additional power if necessary. ... This allows the heat engine of the present disclosure to be mounted on a vehicle to provide motive power or power generation in addition to that of a larger engine, with little weight gain.

The device is inherently very low inertia, which ensures low load and quick and easy starting.

With regard to heat pumps (Examples 1, 3) in FIG. 15, 19 and heat engines (Examples 2, 4) in FIG. 16, 20, their configurations provide particular advantages due to their inherent thermodynamic reversibility. Thus, the devices can operate with working fluids in different phases (for example, in different phase states) in any direction. Thus, the range of applications of the devices according to the present invention can be wider than that of the known devices.

Therefore, a mechanically simple and scalable device is provided for cooling or power generation purposes. In addition, heat pumps or heat engines according to the present disclosure can have high efficiency in any of the modes of operation.

With regard to heat engines (Examples 2, 4-8) in FIG. 16, 21-24, the device of the present disclosure provides a high thermodynamic efficiency solution capable of operating at low rpm. Low speed operation provides the advantage of being able to generate electricity at or near the required speed, which reduces gear and signal inversion dependencies and associated losses.

The rotor 14 and the casing 12 can be made with a small gap between them. The dry and vacuum capability eliminates the need for contact seals between rotor 16 and casing 12 and thereby minimizes frictional losses.

For applications where this can be advantageous, the shaft 18, 118, 218 may extend from both sides of the rotor housing in a powertrain-coupled manner to drive a device and / or an electric generator.

EXAMPLE 9 - SINGLE UNIT, OPEN CIRCUIT, AIR CYCLE

FIG. 25 illustrates an example of an open loop air cycle apparatus 1000 according to the present disclosure, which includes a variety of features in common with the example of FIG. 21 or equivalent, for which the same position numbers are used.

The system is an open loop, with no communication between the first window 114a and the fourth window 116b. In other words, the second passage 304a and the second heat exchanger 306a are absent, whereby the first port 114a and the fourth port 116b are isolated from each other.

A motor 308 is coupled to a first shaft portion 118 to rotate the rotor 119 about a first axis of rotation 130.

In this example, the first chamber 134a and the first piston element 122a define the first flow portion 111, in this example configured to function as a compressor or displacement pump. Thus, the first flow portion 111 is configured to allow fluid to pass from the first port 114a to the second port 114b through the first chamber 134a.

In addition, the second chamber 134b and the second piston member 122b form a second flow portion 115, in this example configured to function as a metering portion or expansion portion. Thus, the second flow portion 115 is configured to allow fluid to pass from the third port 116a to the fourth port 116b through the second chamber 134.

The first port 114a may be in fluid communication with an ambient air source, for example, to the atmosphere. Therefore, in this example, the working fluid may include air. However, in other examples, the fluid can be any suitable fluid.

The first heat exchanger 302a may be thermally associated with any suitable heat source or substance to be cooled. In one example, a substance, such as a second fluid to be cooled, is passed through a channel 303 in a first heat exchanger 302a so that the substance can transfer heat to the working fluid, thereby cooling the specified substance as it passes through the first heat exchanger 302. The specified substance may be any medium capable of flowing and cooling, for example, a fluid such as air, gas or liquid. In some examples, the specified substance is an environment for lowering the ambient temperature in the home, for example, for regulating the temperature in buildings. In other examples, the substance can serve to cool or heat electronic systems.

Thus, the first heat exchanger 302a is a heat source capable of transferring thermal energy to a working fluid passing through it.

The volumetric capacity of the first chamber 134a may be substantially equal to, less than or greater than, the volumetric capacity of the second chamber 134b.

In other words, in this example, the volumetric capacity of the second flow portion 115 may be equal to the volumetric capacity of the first flow portion 111, be less or greater than it. In this example, the volumetric capacity of the second flow portion 115 is preferably greater than the volumetric capacity of the first flow portion 111.

For example, the volumetric capacity of the second chamber 134b may be no more than half the volumetric capacity of the first chamber 134a of the first rotor.

In other examples, the volumetric capacity of the second chamber 134b may be no more than 20% of the volumetric capacity of the first chamber 134a of the first rotor.

Alternatively, the volumetric capacity of the second chamber 134b of the first rotor may be at least twice the volumetric capacity of the first chamber 134a of the first rotor.

Alternatively, the volumetric capacity of the second chamber 134b of the first rotor may be at least three times the volumetric capacity of the first chamber 134a of the first rotor.

In this example, this provides some degree of expansion within a single device (eg, disclosed in FIG. 17).

This can be achieved by making the first chamber 134a different in width from the width of the second chamber 134b, whereby, as a consequence, the width of the first piston element 122a will be different from the width of the second piston element 122b. Therefore, although the piston members rotate and thus move by the same amount about the second axis of rotation 132, the volume of the chambers 134a, 134b and the working volume of the first and second piston members 122a, 122b will be different from each other.

Different volumes can be achieved by making the second chamber 134b wider than the first chamber 134a, thereby making the second piston element 122b wider than the first piston element 122a.

Therefore, although the piston elements will rotate and thus move by the same amount about the second axis of rotation 132, the volume of the second chamber 134b will be greater than the volume of the first chamber 134a and thus the working volume of the second piston element 122b will be greater than the first piston element 122a.

Since the first flow path 111 (in this example, the displacement / compressor / pump portion) and the second flow path 115 (in this example, the metering / expansion portion) are two sides of the same rotor, the rotor 119 drives both the motor and dosing / expanding the fluid in the second chamber 134b (i.e., in the subchambers 134b1, 134b2).

The operation of the device 1000 will be disclosed below.

Stage 1

In the example of FIG. 25, working fluid (eg, air) enters the subchamber 134a1 through the first port 114a.

Next, the working fluid is displaced / compressed / dispensed by the first piston element 122a driven by the motor 308, the working fluid expands in the second chamber 134b (as disclosed below in Step 3) and exits through the second port 114b.

Simultaneously with the withdrawal of the working fluid into the subchamber 134a1, the working fluid is discharged from the subchamber 134a2 through the second window 114b.

Simultaneously with the discharge of the working fluid from the subchamber 134a2, the working fluid is taken into the subchamber 134a1 through the first window 114a.

Stage 2

In the example of FIG. 25, the working fluid then flows from the first chamber 134a through the channel 300a1 and enters the first heat exchanger 302a, which is configured as a heat source. Therefore, heat is transferred to the working fluid as it passes through the first heat exchanger 302a.

A substance, such as air, gas or liquid, can also be passed through the heat exchanger 302a through a separate inlet and serves to transfer heat to the working fluid. In other words, the substance enters the heat exchanger 302a at the first temperature and leaves the heat exchanger at the second temperature, while the second temperature is lower than the first. The heat from the substance is transferred to the working fluid. Thus, the working fluid absorbs heat from a heat source (such as a specified substance), and then leaves the first heat exchanger 302a and passes through the channel 300a2, before entering the second chamber 134b.

Stage 3

In the example of FIG. 25, working fluid exits the first heat exchanger 302a through passage 300a2. The pressure of the working fluid is maintained at a relatively low pressure in the channel 300a2, for example, below atmospheric pressure.

The working fluid flows through the channel 300a2 and through the third window 116a enters the rotor subchamber 134b1, where the working fluid expands.

Simultaneously with the entry of the working fluid into the subchamber 134b1 and its expansion therein, the working fluid is discharged from the subchamber 134b2 through the fourth port 116b.

As the rotor 119 continues to rotate, the working fluid is released from the subchamber 134b2 through the fourth port 116b, and through the third port 116a, more working fluid enters the subchamber 134b1, where it expands.

Thus, there is a sequential expansion of the exhaust gas in the subchambers 134b1, 134b2 of the second chamber 134b (i.e., a drop in fluid pressure and an increase in its volume). In one example, the effect of this expansion is to maintain a vacuum in the passage 300a, which in turn helps to drive the first piston element 122a through the chamber 134a and thereby introduce more air to restart the process. Expansion of the exhaust gas in the subchambers 134b1, 134b2 may cause the fluid to act on the second piston element 122b to force the second piston element 122b through chamber 134b (functioning as an expansion chamber), which drives the first piston element 122a through the first chamber 134a to extraction and compression of the next portion of air to start the process again.

Thus, the successive expansion of the working fluid in the subchambers 134b1, 134b2 of the rotor creates a force under which the rotor rotates about its second axis of rotation 132 and the rotor rotates about its first axis 130 of rotation. This rotation force is in addition to the 308 motor.

Thus, the system of FIG. 25 is configured to function as a cold air supply pump.

During operation, the system in FIG. 25 is reversible, and therefore, in the event of a change in the direction of rotation of the motor 308, a positive pressure difference arises between the second flow path 115 and the first flow path 111. In this example, the heat exchanger 302 extracts heat from the fluid passing through it to heat the substance in the channel 303. In this example, the system is an air source heat pump. In other words, the motor 308 can be reversible. When the motor 308 can drive the rotor 119 about the first axis of rotation 130 in the first direction, the first heat exchanger 302a can function as a heat source for transferring heat from the specified substance to the fluid.

Since the system is reversible, when the motor can drive the rotor 119 about the first axis of rotation 130 in a second direction opposite to the first direction, the first heat exchanger 302a can function as a heat source to transfer heat from the fluid to the specified substance. In this example, the system is configured to function as an air source heat pump.

FIG. 26 depicts a partial exploded view of an alternative example of a core 510 included in an apparatus according to the present disclosure. The core 510 includes a shroud 512 and a rotor assembly 514. FIG. 27A and 27B are side and cross-sectional views of an example of shroud 512 as it encloses rotor assembly 514.

In the example of FIG. 26, the casing 512 is divided into three portions 512a, 512b and 512c enclosing the rotor assembly 14. Alternatively, the casing may be made of more than two parts and / or not divided as shown in FIG. 26. In this example, the first shroud end 512a and the second shroud end 512b may be connected to the intermediate ring 512c during operation. In some examples, the first shroud end 512a and the second shroud end 512b may be attached to the spacer ring 512c. In this example, the outer race of bearing 529 is connected to the spacer ring 512c. In one example, an outer bearing race is formed on the inner surface of the spacer ring 512c or shroud 512.

Piston element 522 and technical axis 520 are substantially identical to piston element 22 and technical axis 20 in FIG. 8-10. In this example, one or more bearings 521 can be located on the rotor 516 to allow rotation of the technical axis 520 relative to the rotor 516. The bearing axis journal 523 can be placed in one or more bearings 521 to axially fix the technical axis 520 relative to the rotor 516, while allowing rotational movement about axis 532. In some examples, a cover 525 may be fitted over the bearing axis journal 523 and bearing 521.

In this example, the orbital slewing ring 527A, 527B may be circumferentially located outside the rotor 516. In the disclosed example, the orbital slewing ring includes a first ring 527A and a second ring 527B configured to be coupled to an inner bearing race 529. In some examples the first ring 527A and the second ring 527B are attachable to each other to secure at least a portion of the bearing 529 therebetween. In one example, the first guide means (552) may include a pin configured to receive or connect to a pivot ring (527).

In this example, the second guide means 550 includes an orbital slewing ring 527A, 527B and a bearing 529, which may be formed by an inner race, an outer race, and a rolling element.

During operation, the first guide means 552 may be mechanically coupled to the second guide means 550. In some examples, the first guide means 552 includes a pin adapted to be received in the orbital slewing ring 527 to connect the rotor 516 to the orbiting slewing ring 527A , 527B. Bearing 529 forms a guide path for pivoting rotor 516 about shaft 522 about axis 530.

As disclosed in FIG. 27A and 27B, the guide path formed by connecting the first guide means 552 and the second guide means 550 may be a path around the first circumference of the casing 512 (i.e., on, near and / or on either side of it).

The creation of the support track formed by the first guide means 552 and the second guide means 550 reduces friction and noise, vibration and roughness of the device.

Bearing 529 can be in any shape, such as a rolling element, ball, or other frictionless element, or it can be a bushless bearing. The example shows a pair of angular contact ball bearings installed back to back.

In some examples, a pair of back-to-back angular contact bearings provide greater speed tolerance, greater load tolerance, larger rolling element size, with the raceway load being distributed over a larger area rather than concentrated in a single point. In addition, this makes it possible to reduce the dead space inside the device due to the fact that there is no or essentially no play, since both sides of the bearing are in constant contact with each other. The bearing can also serve to hold the rotor 516 in the center of the interior of the casing 512 so that the thermal expansion is the same in any direction from the center point.

The directionality of the guide path determines the linear change, amplitude and frequency of turns of the rotor 516 around the second axis of rotation 532 in relation to rotation around the first axis of rotation 530, thereby determining the ratio of the angle of displacement of the chambers 534 to the radial movement by means of the shaft (or vice versa) at any point

In other words, the orientation of the path directly determines the mechanical ratio / relationship between the peripheral speed of the rotor and the rate of change in the volume of the chambers 534a, 534b of the rotor. In other words, the path of the path 550 directly determines the mechanical ratio / relationship between the peripheral speed of the rotor 516 and the speed of rotation of the rotor 516.

In this example, the guide path formed by the connection of the first guide means 552 and the second guide means 550 is located at an angle of 30 degrees from the vertical, while in other examples this angle may be different.

Please note that the contents of all materials and documents submitted simultaneously with or prior to this description in connection with this application and posted for public inspection together with this description are incorporated into this document by reference.

All the distinctive features disclosed in this description (including the appended claims, abstract and drawings), and / or all steps of any method or technology disclosed therein, can be combined in any combination, except for those in which at least some of these features and / or steps are mutually exclusive.

Any feature disclosed in the present description (including in any of the appended claims, in the abstract and drawings) can be replaced with alternative features of the same, equivalent or similar purpose, unless explicitly stated otherwise. Thus, unless expressly indicated otherwise, any of the disclosed features is nothing more than an example of a generic group of equivalent or similar features.

The invention is not limited to the details of the above-disclosed embodiment (s). The scope of the present invention includes any new features or any new combinations of features disclosed in this description (including in any of the appended claims, in the abstract and drawings), as well as any new steps or any new combinations of steps disclosed therein. fashion or technology.

Claims (94)

1. Rotational thermodynamic device with a first flow path, comprising: the first shaft part, forming the first axis of rotation and made with the possibility of rotation about it; a first technical axis defining a second axis of rotation, the first shaft portion passing through the first technical axis; a first piston element located on the first shaft portion, the first piston element extending from the first technical axis towards a distal end of the first shaft portion; the first rotor carried by the first technical axle, the first rotor comprising: the first camera, the first piston element passing through the first chamber; the first wall of the casing adjacent to the first chamber, a first window and a second window located in the first wall of the casing, each of them in fluid communication with the first chamber; characterized in that: the first rotor and the first technical axis are made with the possibility of rotation with the first shaft part about the first axis of rotation; wherein the first rotor is configured to rotate relative to the technical axis around the second axis of rotation to provide the first rotor with the ability to rotate relative to the first piston element when the first rotor rotates around the first axis of rotation; whereby the first flow path is configured to allow fluid to pass from the first port to the second port through the first chamber; while the device additionally contains a second flow part containing: second chamber, the second wall of the casing adjacent to the second chamber, a third window and a fourth window located in the second wall of the casing, each of them being connected downstream with the second chamber, whereby the second flow path is made with the possibility of passage of fluid from the third window to the fourth window through the second chamber; wherein the second window is in fluid communication with the third window through the first heat exchanger. 2. A device according to claim 1, wherein the second axis of rotation is substantially perpendicular to the first axis of rotation. 3. A device according to claim 1 or 2, characterized in that: the first rotor further comprises a second chamber; the first piston element extends from one side of the first technical axis along the first shaft portion; wherein the second piston element extends from the other side of the first technical axis along the first shaft part, through the second chamber to allow the first rotor to rotate relative to the second piston element when the first rotor rotates about the first axis of rotation. 4. The device according to claim 3, characterized in that: the fourth port is in fluid communication with the first port through a second heat exchanger. 5. A device according to any one of the preceding claims, characterized in that the first shaft part, the first technical axis and the first piston element are stationary relative to each other. 6. The device according to claim 1 or 2, characterized in that it additionally contains: a second rotor containing a second chamber, the second shaft part with the possibility of rotation about the first axis of rotation; wherein the second shaft part is connected to the first shaft part with the possibility of joint rotation of the first shaft part and the second shaft part about the first axis of rotation; the second technical axis, forming the third axis of rotation, while the second shaft part passes through the second technical axis; a second piston element located on a second shaft portion, the second piston element extending from a second technical axis towards a distal end of the second shaft portion; the second rotor carries the second technical axis; the second piston element passes through the second chamber; so that: the second rotor and the second technical axis are made with the possibility of rotation with the second shaft part about the first axis of rotation; wherein the second rotor is configured to rotate relative to the second technical axis around the third axis of rotation to provide the second rotor with the possibility of rotation relative to the second piston element when the second rotor rotates about the second axis of rotation. 7. A device according to claim 6, wherein the third axis of rotation is substantially perpendicular to the first axis of rotation. 8. A device according to claim 6 or 7, characterized in that: the first rotor additionally contains: the second chamber of the first rotor, a first piston element extending from one side of the first technical axis along the first shaft portion; wherein the second piston element extends from the other side of the first technical axis along the first shaft portion, through the second chamber of the first rotor to allow the first rotor to rotate relative to the second piston element when the first rotor rotates about the first axis of rotation; wherein the second rotor additionally contains: the first chamber of the second rotor, a second piston element extending from one side of the second technical axis along the second shaft portion; wherein the first piston element of the second rotor extends from the other side of the second technical axis along the second shaft portion, through the first chamber of the second rotor to allow the second rotor to rotate relative to the first piston element of the second rotor when the second rotor rotates about the first axis of rotation; moreover: the second chamber of the first rotor is connected downstream with the fifth window and the sixth window; to thereby enter into the composition of the first flow part and is made with the possibility of passing the fluid from the fifth window to the sixth window through the second chamber of the first rotor; the first chamber of the second rotor is connected downstream with the seventh window and the eighth window; to thereby be incorporated into the second flow path and is configured to allow fluid to pass from the seventh port to the eighth port through the first chamber of the second rotor; wherein the sixth port is in fluid communication with the seventh port through the first heat exchanger. 9. The device of claim. 8, characterized in that the eighth window is in fluid communication with the fifth window through the second heat exchanger. 10. A device according to claim 9, wherein the fourth port is in fluid communication with the first port through a second heat exchanger. 11. Device according to any one of paragraphs. 6-10, characterized in that the first shaft part is directly connected to the second shaft part, in connection with which the first rotor and the second rotor are made with the possibility of rotation only at the same frequency. 12. Device according to any one of paragraphs. 6-11, characterized in that the second shaft part, the second technical axis and the second piston element are stationary relative to each other. 13. Device according to any one of paragraphs. 1-12, characterized in that the first heat exchanger is configured to function as a heat sink for extracting heat energy from a fluid passing through it. 14. The apparatus of claim 13, wherein the second heat exchanger is configured to function as a heat source for transferring thermal energy to a fluid passing through it. 15. A device according to claim 13, wherein the first heat exchanger comprises: a chamber configured to pass a fluid flow from the first flow portion to the second flow portion; and a nozzle capable of injecting a cryogenic medium into the chamber, as a result of which heat energy is transferred from the fluid to the cryogenic media. 16. Device according to any one of paragraphs. 1-12, characterized in that the first heat exchanger is configured to function as a heat source for transferring thermal energy to a fluid passing through it. 17. The device according to claim 13, characterized in that the second heat exchanger is configured to function as a heat sink for extracting thermal energy from a fluid passing through it. 18. The device according to claim 16, characterized in that the first heat exchanger comprises a combustion chamber capable of continuous combustion. 19. A device according to any of the preceding paragraphs, characterized in that: the chamber or each of the chambers contains an opening; in this case, the corresponding piston element or each of them extends from its technical axis through the corresponding chamber towards the corresponding opening. 20. Device according to any one of paragraphs. 1-19, characterized in that it additionally contains: a rotary actuator configured to rotate the rotor relative to the technical axis; moreover, the rotary actuator contains: the first guide means located on the rotor; and second guiding means located on the first wall of the casing and / or the second wall of the casing; wherein the first guiding means is configured to interact with the second guiding means for rotating the rotor about the technical axis. 21. Device according to any one of paragraphs. 1-19, characterized in that it additionally contains: a rotary actuator configured to rotate the rotor relative to the technical axis; moreover, the rotary actuator contains: the first guide means on the rotor; and a second guide means located on the first wall of the casing and / or the second wall of the casing; the first guide means complement the second guide means in shape; wherein one of the first and second guide means forms a path along which the other of the first and second guide means is forced to follow; wherein the other of the first and second guide means comprises a rotatable element configured to engage with the tract and rotate as it moves along the tract. 22. A device according to claim 20 or 21, characterized in that the second guide means comprises a pivot ring configured to support at least a part of the bearing connected to the first wall of the casing and / or the second wall of the casing. 23. A device according to claim 22, characterized in that the first guide means comprises a pin adapted to be connected to the pivot ring. 24. The device according to claim. 16, characterized in that the heat source contains a substance passing through a channel in the first heat exchanger, and the device provides cooling of the substance. 25. A device according to claim 24, wherein the fluid contains air. 26. A device according to claim 24 or 25, characterized in that the device comprises a motor connected to the first shaft part with the possibility of driving the rotor around the first axis of rotation. 27. The device according to claim 26, characterized in that the motor is reversible, whereby when the motor is configured to drive the rotor around the first axis of rotation in the first direction, the first heat exchanger is provided for the function of the first heat exchanger as a heat source for transferring heat from said fluid environment, wherein when the motor is configured to drive the rotor about a first axis of rotation in a second direction opposite to the first direction, the first heat exchanger is provided to function as a heat sink for transferring heat from the fluid to said substance. 28. A device according to any of the preceding claims, characterized in that the first flow path and the second flow path are two sides of the first rotor, one of the first flow path and the second flow path being configured to function as a compressor, and the other from the first flow path and the second flow path is configured to function as an expander.

Images